DE102017006206A1 - Positive displacement compressor system for R-718 - Google Patents

Abstract

The invention relates to the compression of water vapor as R-718 in particular for the refrigeration and heat pump technology. In order to improve efficiency and safe operation at the same time greater pressure range under all working conditions, a 2-shaft displacement machine with electronic motor pair spindle rotor synchronization as R718 Verdrängerverdichtersystem (42) with open compressor machine (41) is proposed according to the invention, the evaporator (7) and condenser (8) separated from each other, wherein the drive motors (2.3 and 3.3) on the inlet side (11) project fully into the space of the evaporator (7), and ensures a heat balance management at all operating points for the "unlimited" operation, esp. In k ₀ operation, and preferably by centrifugal disc (22) a cooling fluid flow (9.4) is supplied to the inlet side, and via control balls (10) the internal compression ratio Π _{i is} constantly adjusted with outlet gap IV adjustment , and the rotor profile flanks with a tooth flank offset Δk _vs (z) between the profile flank sides of a profile tooth i Rotor longitudinal axis direction are executed, the spindle rotors in order to adapt to the respective application requirements belong to a rotor assembly and PIRSA (= "Pressure-InnerRatio-Speed-Adaption") the efficiency is improved.

Description

State of the art:

The refrigeration market is currently changing and so is the so-called. "F-gas regulation" according to Regulation (EC) No. 842/2006 and No. 517/2014 on fluorinated greenhouse gases as a challenge on everyone's lips, in order to suppress the prevailing refrigerants HFC and HFO because of their climate and environmental harmfulness. Therefore, there is a strong desire in the refrigeration for natural refrigerants, in particular water impresses with its good thermodynamic properties.

So far, the thorough realization of water as refrigerant R-718 but failed because, for example, compared to ammonia in the same function by about 300-fold larger delivery volume flow at the same power is required. By at the same time the pressure ratio as possible above factor 10 is quite high, the demands on a compressor increase enormously, which must be at the same time still oil-free and has to work as efficiently as possible in the vacuum, namely between 6 mbar and 200 mbar and possibly even higher.

• • mobile Kälte-/Klima-Technik (also für Bahn, LKW und PKW)
• • stationäre Kältetechnik (also Industriekälte, Gewerbekälte und Gebäudeklimatisierung, Wärmepumpen)

The disruptive nature of water as a refrigerant is undisputed and will abruptly end the worldwide intensive discussions on the known environmental and climate problems in today's refrigerants. At the same time, the refrigeration technology can be transferred 2 represent large areas:

• • mobile refrigeration / air conditioning technology (ie for trains, trucks and cars)
• • stationary refrigeration (ie industrial refrigeration, commercial refrigeration and air conditioning, heat pumps)

So far it tries to meet this challenge over turbo compressors, whereby these machines despite 2 -stufiger design with intermediate cooling only lower pressure conditions of about 6 create, so that in the refrigeration cycle, the necessary heat transfer to the capacitor is implemented only unsatisfactory. In addition, there is the serious disadvantage of a turbomachine with regard to the soft working characteristic (ie pressure values over volume flow) in order to be able to ensure stable operating points for different operating points.

• • Förderung hoher Wasserdampf-Volumenströme von weit über 5.000 m³/h für beispielsweise 35 kW Kälte-Leistung, was gegenüber dem Stand der Technik mindestens 60-fach höher ist. Damit sind sowohl bei den Drehzahlen als auch zur Geometrie-Ausführung der Verdrängermaschine neue Wege zu beschreiten.
• • Beherrschung großer Druckverhältnisse von deutlich über 10 bei niedrigen Verdampfer-Temperaturen und höheren Temperaturen im Kondensator. Weil bei Wasserdampf zugleich der Isentropenexponent größer als 1,32 ist (heutige Kältemittel liegen bei etwa 1,1 und haben damit kaum Temperatur-Stress), ergeben sich rechnerisch für Kältemittel R-718 sehr hohe Verdichtungsendtemperaturen von deutlich über 200°C, die nicht nur den Wirkungsgrad des Verdichters beeinträchtigen, sondern auch insbes. die empfindliche Verdichterbauteile (besonders die Rotorlagerung auf der Auslass-Seite) gefährden.
• • Der Kältemittel-Kreislauf muss für R-718 (= Wasserdampf) vollständig ölfrei sein, was bei 2-Wellen-Verdrängermaschinen eine Herausforderung darstellt, weil dieser Maschinentyp bei Verzicht auf ein Betriebsfluid (heutzutage zumeist Öl) eine trockene Synchronisation für das Spindelrotorpaar braucht, um eine Berührung zwischen den schnell drehenden Spindelrotoren zu vermeiden.

Undoubtedly, a water vapor compression displacement machine is the better solution to tackle the challenges of water vapor compression in R718 refrigeration cycles. The following serious challenges have to be solved for the compression of water vapor as refrigerant R-718:

• • Promotion of high water vapor volume flows of well over 5,000 m ³ / h for example, 35 kW cooling power, which compared to the state of the art at least 60 -fold is higher. This means breaking new ground both in terms of speed and the geometry of the positive displacement machine.
• • Control of large pressure ratios from well above 10 at low evaporator temperatures and higher temperatures in the condenser. Because at steam at the same time the isentropic exponent larger than 1.32 is (today's refrigerant is about 1.1 and thus have little temperature stress), calculated arise for refrigerant R-718 very high compression end temperatures of well above 200 ° C, which not only affect the efficiency of the compressor, but also esp. the sensitive compressor components (especially the rotor bearing on the outlet side) endanger.
• • The refrigerant cycle must be 718 (= Water vapor) to be completely oil-free, which is at 2 Wave displacement machines is a challenge, because this type of machine waives a dry operating fluid (now mostly oil) a dry synchronization for the spindle rotor pair to avoid contact between the high-speed spindle rotors.

Object of the present invention:

1. (1) Sichere Vermeidung der Spielaufzehrung beim Verdichter:
   • Die Spielaufzehrung führt beim Verdichter zum Ausfall als sogen. „Crash“ durch Berührung der Arbeitsraum-Bauteile, indem die Spaltwerte zwischen den Arbeitsraum-Bauteilen von den üblichen Millimeter-Bruchteilen auf Null gehen, wenn auch nicht überall, sondern nur dort, wo die zumeist thermischen Dehnungen kombiniert mit Rundlauffehlern und anderen Abweichungen unter der Vielfalt der verschiedensten Einfluss-Parameter dazu führen können. Diese Spielaufzehrung ist mit genügend Sicherheitsreserve für ausnahmslos sämtliche Betriebs-, Arbeits- und UmgebungsBedingungen jederzeit zuverlässig und vollumfänglich als absolute Muss-Aufgabe zu vermeiden.
2. (2) Bestmögliche Effizienz, also optimaler Wirkungsgrad für das R718-Verdrängerverdichtersystem:
   • Dies betrifft neben dem Betreiben bei optimal angepassten Betriebsparametern insbes. die Minimierung der Systemverluste und dabei hauptsächlich den Einfluss der inneren Spaltleckagen, die den Wirkungsgrad beeinträchtigen, ohne dabei aber das Muss-Ziel zur Crash-Vermeidung zu gefährden.
3. (3) Größte Zuverlässigkeit und hohe Lebensdauer (lange Standzeit) des R718-Systems:
   • Hierbei sind vornehmlich die empfindlichen Bauteile zu schützen, insbesondere die Rotor-Lagerung (speziell auf der Auslass-Seite) und die beiden Antriebsmotore mit dem jeweiligen Equipment
4. (4) Weitestgehend*°* unabhängig von den äußeren Einsatz-Bedingungen in dem Sinne, dass sich das R718-Verdrängerverdichtersystem an die unterschiedlichsten Bedingungen selbständig anpasst. *°* weitestgehend derart, dass es praktisch keine Einschränkungen bei den Einsatz-Bedingungen gibt.
5. (5) System-Intelligenz:
   • Das R718-Verdrängerverdichtersystem muss selbständig durch eigene Regulier-Mechanismen und Regulier-Werkzeuge in der Lage sein, jederzeit und unter allen Umständen die zuvor genannten Aufgaben zu erfüllen bzw. im Falle drohender Abweichungen rechtzeitig eigene Abhilfemaßnahmen einzuleiten bis hin zu Warnungen und Hinweise nach außen abzugeben.

The following tasks have to be solved for the R718 positive displacement compressor system:

1. (1) Safe avoidance of game consumption on the compressor:
   • The Spielaufzehrung leads the compressor to failure as so-called. "Crash" by touching the work space components by the gap values between the work space components from the usual millimeter fractions to zero, if not everywhere, but only where the mostly thermal strains combined with concentricity errors and other deviations under the Variety of different influence parameters can lead to it. This Spielaufzehrung is with sufficient safety margin for all operating, working and environmental conditions without exception reliably and completely as an absolute must-task to avoid.
2. (2) Best possible efficiency, ie optimum efficiency for the R718 positive displacement compressor system:
   • In addition to operating with optimally adjusted operating parameters, this particularly concerns the minimization of system losses and, at the same time, mainly the influence of internal gap leakage, which adversely affects the efficiency, but without jeopardizing the must-have goal for crash avoidance.
3. (3) Highest reliability and long life (long life) of the R718 system:
   • Hereby, primarily the sensitive components have to be protected, in particular the rotor bearing (especially on the outlet side) and the two drive motors with the respective equipment
4. (4) As far as possible * ° * regardless of the external conditions of use in the sense that the R718 positive displacement compressor system adapts itself to a wide range of conditions. * ° * as much as possible so that there are practically no restrictions on the conditions of use.
5. (5) System intelligence:
   • The R718 Positive Displacement Compressor system must be able to perform the aforementioned tasks at any time and under all circumstances by its own regulating mechanisms and regulating tools, or to initiate its own corrective measures in the event of imminent deviations, as well as to issue warnings and instructions to the outside ,

• ► Verdampfer (7) mit Verdampfer-Gehäusetopf (29)
• ► Kondensator (8) mit Kondensator-Gehäusetopf (28)
• ► und Verdichtermaschine (41), wobei diese Verdichtermaschine im Wesentlichen besteht aus:
  • • Verdichtergehäuse (1)
  • • zwei eigenständige Rotationseinheiten (39 und 40) mit elektronischer Motorpaar-Spindelrotor-Synchronisation über die FUs (2.4 bzw. 3.4) mit der FU-Control-Unit (16)
  • • und Auslass-seitige Lagerträger-Einheit(en) (25) zur Aufnahme der Rotorlager (4.2) und dem Auslass (12) mit Auslass-Öffnungen über Steuerkugeln (10) sowie End-Auslass-Öffnungen (27)
    
    und alles wird von der Control-Unit (15) geführt.

This object is achieved according to the invention for the compression of water vapor at pressures below atmospheric pressure by a 2 Shaft rotary displacement machine solved by the R718 Verdrängerverdichtersvstem ( 42 ) is executed as a closed vacuum system consisting of the core components:

• ► evaporator ( 7 ) with evaporator housing pot ( 29 )
• ► Capacitor ( 8th ) with condenser housing pot ( 28 )
• ► and compressor machine ( 41 ), this compressor machine essentially consisting of:
  • • compressor housing ( 1 )
  • • two independent rotation units ( 39 and 40 ) with electronic motor pair spindle rotor synchronization via the drives ( 2.4 respectively. 3.4 ) with the FU control unit ( 16 )
  • • and outlet side bearing support unit (s) ( 25 ) for receiving the rotor bearings ( 4.2 ) and the outlet ( 12 ) with outlet openings via control balls ( 10 ) as well as end outlet openings ( 27 )
    
    and everything is handled by the control unit ( 15 ) guided.

In doing so, this compressor machine ( 41 ) According to the invention designed as an open machine with the compressor housing ( 1 ) the evaporator ( 7 ) and the capacitor ( 8th ) separates. Thus, the compressor machine so no frontal Verdichterbegrenzungs side panels (so-called "cover") more and is no longer self-sufficient to operate as a vacuum machine, but only in conjunction with a connected evaporator ( 7 ) and connected capacitor ( 8th ) with respective housing pot ( 28 and 29 ).

In addition, the drive motors ( 2.3 respectively. 3.3 ) per spindle rotor rotation unit ( 40 respectively. 39 ) on the compressor intake side ( 11 ) and directly in the evaporator space ( 7 ) suspended for best possible cooling of the electric drive motors ( 2.3 respectively. 3.3 ) for the "unlimited" operation according to the invention in that at elevated (ie above the rated load) power requirements during operation, the heat loss of these drive motors ( 2.3 respectively. 3.3 ) is discharged via the respective cooling fluid flow ❺. Preferably, the monitoring of these drive motors ( 2.3 respectively. 3.3 ) via temperature sensors in the region of the motor windings in order accordingly to be able to adapt the respective cooling fluid flow ❺ in such a way that the drive motors can not be damaged and can provide the required power.

For this heat management according to the invention for the R718 Verdrängerverdichtersystem also belongs to the intermediate water jacket ( 5 ), preferably with its own cooling coil ( 6 ) via the cooling fluid flow ❶ the targeted thermostating the compressor housing ( 1 ) to operate. With simultaneous possibility of means of cooling fluid flow ❷ and ❸ (as 9.2 and 9.3 ) targeted internal rotor cooling ( 2.2 and 3.2 ), the game situation between the working space components (ie compressor housing and spindle rotor pair) and the inner gap leakage thus the degree of delivery for the various operating / operating points due to the respective thermal expansion behavior of the components (which in the Control Unit ( 15 ) for regulating the cooling fluid flows ( 9 ) is deposited with simultaneous secure crash avoidance (crash as a destructive Spielaufzehrung).

• 9.1 Kühlfluidstrom (als ❶ dargestellt) zum Zwischenwassermantel (5) via Kühlrohrschlange (6)
• 9.2 Kühlfluidstrom (als ❷ dargestellt) zum 2z-Rotor (2) via Verdampfer-Kühlbohrung (2.2)
• 9.3 Kühlfluidstrom (als ❸ dargestellt) zum 3z-Rotor (3) via Verdampfer-Kühlbohrung (3.2)
• 9.4 Kühlfluidstrom (als ❹ dargestellt) zur Einspritzkühlung via Schleuderscheibe (22)
• 9.5 Kühlfluidstrom (als ❺ dargestellt) zur Kühlung jedes Antriebsmotors
• *°* Als „Maximal“-Version gelten die Einsatzfälle mit einer besonders großen Einsatz-Bandbreite, wenn also der sogen. „Temperatur-Hub“ (als Differenz zwischen t_c und t₀ ) größer als etwa 40 Kelvin ist, wobei kleinere Maschinen (also mit Fördervolumenstrom unter etwa 5.000 m³/h bei Nenndrehzahl) hierbei unempfindlicher sind, also höhere „Temperatur-Hübe“ problemloser schaffen werden.

In order to fulfill the "unlimited" operation while at the same time offering the best possible degree of efficiency and safe crash avoidance, the heat management system according to the invention for the R718 positive displacement compressor system in the "maximum" version * ° * consists of the following per control unit ( 15 ) specifically regulated cooling fluid streams ( 9 ):

• 9.1 Cooling fluid flow (shown as ❶) to the intermediate water jacket ( 5 ) via cooling coil ( 6 )
• 9.2 cooling fluid flow (shown as ❷) to 2z rotor ( 2 ) via evaporator cooling bore ( 2.2 )
• 9.3 Cooling fluid flow (shown as ❸) to the 3z rotor ( 3 ) via evaporator cooling bore ( 3.2 )
• 9.4 cooling fluid flow (shown as ❹) for injection cooling via centrifugal disc ( 22 )
• 9.5 Cooling fluid flow (shown as ❺) for cooling each drive motor
• * ° * The "maximum" version is defined as the cases of use with a particularly high bandwidth of use, ie if the so-called "Temperature-Hub" (as difference between t _c and t ₀ ) greater than about 40 Kelvin is, with smaller machines (ie with volume flow below about 5000 m ³ / h at nominal speed) are insensitive, so higher "temperature strokes" will create trouble.

This heat management system is particularly urgent for the working space components in the so-called k ₀ operation, when the compressor is operated at a speed that already creates the pressure difference between inlet and outlet but still no or only minimal flow rate promotes, therefore, the compressor only fights with its own (inner) leakage, but due to the power input would be correspondingly hot, which by the control unit ( 15 ) guided heat management according to the invention is reliably prevented.

As a result of this heat balance management, which is practically independent of external conditions, according to the invention the said "unlimited" operation is achieved because at the same time the compressor machine ( 41 ) virtually any pressure ratio and thus virtually any pressure value with the appropriate temperature in the condenser achieved in order to dissipate the amount of heat under virtually all environmental conditions can. This is the so-called. "Unlimited" operation, as it does not exist in the prior art. As an example, the former failures of the air conditioning systems on ICE trains were mentioned because their air conditioning systems did not manage the higher outside temperatures. This can no longer happen with the solution according to the invention.

Moreover, for speed-optimized introduction of the injection cooling amount ❹ according to the invention a centrifugal disc ( 22 ) preferably on each spindle rotor on the conveying gas inlet side ( 11 ), wherein the cooling fluid flow O-feed according to ( 23.1 ) or ( 23.2 ) on the preferably rough slinger surface for a speed-optimized cooling fluid flow-O-mist, which is mixed sufficiently uniformly the conveying gas flow. By "speed optimized" is meant that the velocity vectors of the liquid cooling fluid flow O-mist droplets move similar to the spindle rotor surfaces, for which each centrifugal disc ( 22 ). Thus, a hard impact due to high speed differences on the spindle rotor surfaces is reliably avoided and thus at least an unpleasant Perturbation noise up to the damage of the spindle rotor surfaces.

In addition, there is a tooth flank offset in rotor longitudinal axis z Δk _vs (z) between left and right side of the profile flank such that the head angle be.2K (z) at 2 toothed spindle rotor head bow for the invention be.2K.em (z) run, whereas for selected courses for μ.2 (z) and μ.3 (z) with corresponding tooth height h (z) of be.2K.stu ( z) run results if there is no tooth flank offset. By taking the difference between be.2K.em (z) and be.2K.stu (z) as Δ.be.2K (z) run in conjunction with the slope curve m (z) and the course of the tooth heights h (z) is formed in the rotor longitudinal axis direction, it can be seen that both the be.2K.em (z) run and the Δ.be.2K (z) run are carried out in a simplified opposite manner to the gradient m (z):

At a maximum for m (z), both the be.2K.em (z) run and the Δ.be.2K (z) run are minimal. And when m (z) increases, both the be.2K.em (z) run and the Δ.be.2K (z) run are decreasing, whereas in the inlet area, when m (z) drops sharply, both the be.2K.em (z) run as well as the Δ.be.2K (z) run increase sharply. This feature of the invention applies with an accuracy of preferably ± 15% and ensures on the inlet side ( 11 ), ie in the form of representation chosen here for the range of larger z-values, for higher volumes of the inlet-side working chambers in order to be able to suck in larger delivery volume flows.

For this purpose, in the inlet area of the compressor machine ( 41 ) for μ.3 (z) also values above 0.6 (for example 10% to 15% higher) are proposed so that the intake volumes continue to increase.

Furthermore, according to the invention control balls ( 10 ) for application-specific targeted adjustment of the internal compression ratios, ie in particular at different pressure values in the condenser as different operating points during operation of the R718 Verdrängerverdichtersystems. The internal volume ratio is initially, without consideration of thermodynamic influences, dependent on the executed rotor pair geometry as a simple quotient of inlet to outlet working chamber volume, which is determined in the manufacture of the spindle rotor pairing. By now different operating points with different pressure conditions (as outlet pressure p ₂ divided by the inlet pressure p ₁ ), the control balls ( 10 ) that the efficiency-reducing over-compression is avoided by during compaction when the current outlet pressure is reached p ₂ in the respective working chamber, the control ball is lifted due to the pressure difference, so that a partial gas flow, the working chamber in the direction of Auslassraum ( 12 ) and thus to the capacitor ( 8th ) leaves. This is preferably done both in Rotorlängsachsrichtung and the front side at the outlet end ( 12 ) according to the exemplary illustration in 2 shown. The control balls ( 10 ) are lifted by the pressure difference between the current pressure in the respective working chamber and the outlet pressure p ₂ preferably weighted and move back due to gravity back, which by the angle according to exemplary representation in 8th is shown, where g shows the gravitational direction. Alternatively, of course, a simple Federanstellung for the control balls can be implemented.

The control balls ( 10 ) in 1 and in 4 are on the outlet side in the outlet control disc ( 12 ) as in 2 in longitudinal rotor axis direction for ΠI _iv adaptation to avoid over-or under-compression which is harmful to efficiency, as well as in an axial plan view in the outlet control disk ( 12 ) and fit the so-called. internal volume ratio Π _iv the application-specific actually applied pressure ratio.

In addition, at the 2 - toothed spindle rotor ( 2 ) an intermediate carrier ( 17 ) proposed for weight reduction, esp. Also as a lower moment of inertia during startup (or deceleration) at the same time high flexural rigidity, for example, from vacuum-compatible fiber composite material, eg as CFRP material.

Furthermore, there will be different applications with different temperature-stroke application areas with different "volume curves" (ie the course of the working chamber volumes between inlet and outlet in Rotorlängsachsrichtung) generally as different application-specific requirements, so that different spindle rotor pair interpretations particularly advantageous in terms of energy-efficient operation and are meaningful. In order not to have to perform their own complete compressor machines, it is proposed according to the invention that different pairs of spindle rotors can be used in the same compressor housing, as exemplified in US Pat 13 shown. This is referred to as a "rotor assembly" and means that for different application cases by simple and direct Spindelrotorpaarwechsel the most individually most efficient adaptation to the respective user requirements is achieved easily.

By "practically the same" is meant that, for example, the crossing angle α (shown in FIG 13 ), but the rotor length and possibly also the diameter profile in rotor longitudinal axis direction may vary with the same compressor housing blank, whereby the simple and rapid implementation of different volume curves over different pairs of spindle rotors is the core purpose for the "rotor assembly". The simple and flexible production of the spindle rotors (generally by turning) is an important feature for easy implementation.

mit entsprechend höheren Druckverhältnissen zumeist kurzzeitig erforderlich sind, kommt es im Verdichter zur sogen. Unterverdichtung (der Druck der letzten Arbeitskammer ist niedriger als der Druck am Auslass) und die letzte Arbeitskammer wird isochor gegen einen höheren Druck am Auslass (12) ausgeschoben. Zur Dämpfung dieses die Verdichtereffizienz mindernden Vorgangs wird erfindungsgemäß vorgeschlagen, dass die Spielwerte im Verdichter-Auslassbereich gezielt erhöht werden um etwa 20 bis mindestens 50% höhere mittlere Spaltabstände, vorzugsweise einfach dadurch realisiert, dass die Außenrotordurchmesser dementsprechend kleiner gefertigt werden über einen Bereich in Rotorlängsachsrichtung, der der 0,3 bis 2-fachen Erstreckung der Auslass-seitigen Arbeitskammerlänge in Rotorlängsachsrichtung entspricht, wobei dies bei stirnseitiger Auslass-Platte mit Lagerträger (25) an der Steuerkante (27.S) durch Anphasen (im Sinne eines Abschrägens) dieser Steuerkante (27.S) ebenso umgesetzt wird.In the case of the spindle rotor pair, its internal volume ratio (ie the simple quotient of working chamber volume at the inlet divided by the working chamber volume at the outlet) is preferably between one to one IV range 2 to maximum 20 limited, wherein on the said control balls ( 10 ) Application-specific adaptation to the respective working / operating point with its actual actual pressure conditions. If now in operation even larger temperature strokes ΔT _h according to $$\mathrm{\Delta }{\text{T}}_{\text{H}}={\text{t}}_{\text{C}}-{\text{<figure-callout id="0" label="t" filenames="DE102017006206A1\_0016.png,DE102017006206A1\_0024.png" state="{{state}}">t</figure-callout>}}_0$$

with correspondingly higher pressure ratios are usually required for a short time, it comes in the compressor for so-called. Under-compression (the pressure of the last working chamber is lower than the pressure at the outlet) and the last working chamber is isochoric against a higher pressure at the outlet ( 12 ) pushed out. In order to damp this process which reduces the compressor efficiency, it is proposed according to the invention that the play values in the compressor outlet region be increased by approximately 20 to at least 50% higher average gap distances, preferably simply realized in that the outer rotor diameters are made correspondingly smaller over a range in Rotorlängsachsrichtung that of 0.3 to 2 -fold extent of the outlet-side working chamber length in Rotorlängsachsrichtung corresponds, and this with front-side outlet plate with bearing carrier ( 25 ) at the control edge ( 27.S) by starting (in the sense of chamfering) this control edge ( 27.S) is implemented as well.

These inventive measures combined with simultaneous limitation of the inner volume ratio range on the spindle rotor pair preferably to the above-mentioned IV range is called

"Outlet gap-iV-adjustment"

designated. In this case, the outer rotor diameter gap adaptation on the pair of rotors preferably takes place in such a way that this diameter adaptation in the outlet direction progressively increases slowly starting from progressively greater values, so that the averaged gap spacings reach the abovementioned increase as the mean value. In particular, this exhaust gap IV adjustment serves to reduce the noise by attenuating the exhaust side pressure pulsations.

On top of that, for the R718 positive displacement compressor system ( 42 ) with its respective pair of spindle rotors preferably for each working / operating point the procedure "PIRSA" proposed: "PIRSA" stands for "Pressure-InnerRatio-Speed-Adaption". It is known that different operating / operating points can be realized by different operating parameters (hereinafter referred to by way of example). Using "PIRSA", the operating parameters are set via the Control Unit ( 15 ) is set such that the power consumption for the R718 positive displacement compressor system (for the application-specific respectively required working / operating point () 42 ) becomes minimal.

• • Regulierung der Kühlfluidströme (9) insbes. zur Einspritzmenge (9.4)
• • Anpassung der Spindelrotordrehzahlen über die CU-FU (16) für ein bestimmtes Saugvermögen
• • Einstellung der Druckwerte im Verdampfer (8) und im Kondensator (9)

As operating parameters, this applies in particular with respect to:

• • regulation of cooling fluid flows ( 9 ) in particular to the injection quantity ( 9.4 )
• • adjustment of the spindle rotor speeds via the CU-FU ( 16 ) for a given pumping speed
• • Setting the pressure values in the evaporator ( 8th ) and in the capacitor ( 9 )

The control unit ( 15 ) has its own preinstalled database and can adjust these operating parameters in a regulative manner, whereby this process is carried out application-specifically by means of trial-and-error, by slightly changing individual values and by the system reaction determining whether the overall efficiency has improved or worsened , In this way, the database is self-learning constantly expanded at each operating point and the system increasingly intelligent in terms of efficiency improvement.

Small explanation of the tooth flank offset Δk _vs (z) per profile flank side:

For each angular position φ belongs to each spindle rotor according to the ratio to a z position as a z (φ) function whose derivation via the following equation then the so-called. Gradient course m (φ) results to each spindle rotor, according to the invention is additionally distinguished between right and left profile edge side on the index s: $$\boxed{{\text{m}}_{\text{s}}\left(\mathrm{\phi }\right)=2\mathrm{\pi }\cdot \frac{{\text{dz}}_{\text{s}}\left(\mathrm{\phi }\right)}{\text{d}\mathrm{\phi }}\approx 2\mathrm{\pi }\cdot \frac{\mathrm{\Delta }{\text{z}}_{\text{s}}\left(\mathrm{\phi }\right)}{\mathrm{\Delta \phi }}}$$

Since the distinction between the right and left profile flank side with respect to the viewing direction and the dependence on the pitch direction (ie right or left ascending) per rotor is difficult and always leads to confusion, the tooth flank offset according to the invention is mapped over the head arc angle be.2K (z) 9 Simplified shown in the plane, however, it is because of the non-parallel spindle rotor axes of rotation is a three-dimensional task.

Small explanation of tooth profile formation: (simplistic as a flat representation)

• am 2z-Rotor: $${\text{R}}_{\text{2K}}\left(\text{z}\right)={\mathrm{\mu }}_2\left(\text{z}\right)\cdot \text{a}\left(\text{z}\right)$$
  
• am 3z-Rotor: $${\text{R}}_{\text{3K}}\left(\text{z}\right)={\mathrm{\mu }}_3\left(\text{z}\right)\cdot \text{a}\left(\text{z}\right)$$
  
• Demgemäß gilt in Rotorlängsachsrichtung z für die Zahnhöhe h(z): $$\text{h}\left(\text{z}\right)=\left({\mathrm{\mu }}_2\left(\text{z}\right)+{\mathrm{\mu }}_3\left(\text{z}\right)-1\right)\cdot \text{a}\left(\text{z}\right)$$
  

The in rotor longitudinal axis direction (generally designated z) different tooth heights h (z) are on the so-called. μ values are generated on each rotor by applying the head radii per spindle rotor:

• at the 2z rotor: $${\text{R}}_{\text{2K}}\left(\text{z}\right)={\mathrm{\mu }}_2\left(\text{z}\right)\cdot \text{a}\left(\text{z}\right)$$
  
• at the 3z rotor: $${\text{R}}_{\text{3K}}\left(\text{z}\right)={\mathrm{\mu }}_3\left(\text{z}\right)\cdot \text{a}\left(\text{z}\right)$$
  
• Accordingly, in the rotor longitudinal axis z for the tooth height h (z): $$\text{H}\left(\text{z}\right)=\left({\mathrm{\mu }}_2\left(\text{z}\right)+{\mathrm{\mu }}_3\left(\text{z}\right)-1\right)\cdot \text{a}\left(\text{z}\right)$$
  

• ► Für $\boxed{{\mathrm{\mu }}_3\left(\text{z}\right)\le \mathrm{0,6}}$
  
  bleibt die Paarung aus 2z-Rotor (2) und 3z-Rotor (3) ohne Blasloch
• ► Um das Einlass-seitige Arbeitskammervolumen zu erhöhen, wird es für einige Applikationen sinnvoll sein, den µ.3(z)-Wert: über diesen Wert von 0,6 zu erhöhen.
• ► Der µ.2(z)-Wert kann frei gewählt werden, wobei über die Zahnhöhen h(z) die verbleibenden Fußkreis-Stärken zu beachten sind unter der Zielsetzung, dass die biegekritischen Drehzahlen je Spindelrotor ausgeführt werden gemäß: $$\boxed{{\mathrm{\omega }}_{\begin{array}{l}\text{kritisch}\\ \text{2-Rotor}\end{array}}=\mathrm{1,5}\cdot {\mathrm{\omega }}_{\begin{array}{l}\text{kritisch}\\ \text{3-Rotor}\end{array}}}\text{ mit }\boxed{{\mathrm{\omega }}_{\begin{array}{l}\text{kritisch}\\ \text{allgemein}\end{array}}=\sqrt{\frac{\text{c}}{\text{m}}}}$$
  
  (vereinfacht)

Preferably, the courses for μ.2 (z) and μ.3 (z) are selected such that the application-specific requirements are optimally met, for example with respect to the working chamber volume and the so-called. "Volume curve" (ie the course of the working chamber volumes in Rotorlängsachsrichtung, esp. The change of these working chamber volumes is to be considered). For μ.3 (z):

• ► For $\boxed{{\mathrm{\mu }}_3\left(\text{z}\right)\le 0.6}$
  
  remains the pairing of 2z rotor ( 2 ) and 3z rotor ( 3 ) without blowing hole
• ► In order to increase the inlet-side working chamber volume, it will be useful for some applications to increase the μ.3 (z) value: above this value of 0.6.
• ► The μ.2 (z) value can be freely selected, whereby the tooth root heights h (z) must take into account the remaining root strengths, with the objective that the critical bending speeds per spindle rotor be carried out according to: $$\boxed{{\mathrm{\omega }}_{\begin{array}{l}\text{critical}\\ \text{2 rotor}\end{array}}=1.5\cdot {\mathrm{\omega }}_{\begin{array}{l}\text{critical}\\ \text{3 rotor}\end{array}}}\text{With}\boxed{{\mathrm{\omega }}_{\begin{array}{l}\text{critical}\\ \text{generally}\end{array}}=\sqrt{\frac{\text{c}}{\text{m}}}}$$
  
  (Simplified)

In particular via the values for μ.2 (z) and μ.3 (z) as well as the rotor length and the rotor masses, the bending-critical rotational speed in the faster-rotating 2z rotor ( 3 ) is 1.5 times higher than the 3z rotor ( 3 ).

With these points, the above-mentioned objects are achieved via the present invention:

1. (1) Sichere Vermeidung der Spielaufzehrung (als sogen. „Crash“ durch Berührung der Arbeitsraumbauteile), indem für die verschiedenen Betriebs-/Arbeitspunkte die unterschiedlichen thermischen Dehnungen der Arbeitsraum-Bauteile bei gemessenen Referenz-Temperatur-Werten durch intelligente Führung der Wärmebilanzen mit in der Control-Unit (15) hinterlegtem Dehnungsverhalten der Arbeitsraum-Bauteile für die verschiedenen Temp.-Niveaus bei dem jeweiligen Betriebs-/Arbeitspunkt arbeiten.
2. (2) Minimierung der inneren Spaltleckage durch Einhaltung eines Spaltbereiches, vorzugsweise in einem Bereich von ± 25%, wobei der untere Wert von der Vermeidung der Spielaufzehrung zzgl. einem Sicherheitsaufschlag abgeleitet wird und im Bereich von 0,05 bis 0,1 mm liegt bei entspr. Rundlauf-Genauigkeiten von vorzugsweise unter 0,02 mm bei Maschinengrößen im Achsabstandsbereich von etwa 100 mm bis ca. 500 mm (darunter ist der Wert entsprechend kleiner, darüber größer)
3. (3) Schutz der empfindlichen Bauteile, insbes. der Rotor-Lagerung (speziell auf der Auslass-Seite) und der beiden Antriebseinheiten durch das beschriebene Purge-Gas-System (30 und 31)
4. (4) weitestgehend*°* unabhängig von den äußeren Einsatz-Bedingungen in dem Sinne, dass sich das R718-Verdrängerverdichtersystem an die unterschiedlichsten Bedingungen selbständig anpasst. *°* weitestgehend derart, dass es praktisch keine Einschränkungen bei den Einsatz-Bedingungen gibt.
5. (5) Intelligente Führung über die Control-Unit (15) insbes. der Kühlfluidströme sowie gemäß PIRSA derart, dass das R718-Verdrängerverdichtersystem in jedem Betriebspunkt den jeweils geringsten Energiebedarf hat, also mit höchster Effizienz arbeitet und zugleich die zuvor genanten Aufgaben erfüllt.

The heat consumption of the work space components, ie housing ( 1 ) and spindle rotor pair ( 2 and 3 ) in the R718 positive displacement compressor system ( 42 ) are managed and regulated in such a way that the following goals are achieved simultaneously and intelligently by the system at all times and under all conditions:

1. (1) Safe avoidance of the Spielaufzehrung (as so-called "crash" by touching the working space components) by the different thermal expansions of the working space components at measured reference temperature values by intelligent management of the heat balances for the various operating / operating points the control unit ( 15 ) of the expansion behavior of the working space components for the different temp. levels at the respective operating / operating point.
2. (2) Minimization of internal gap leakage by maintaining a gap range, preferably in a range of ± 25%, the lower value being derived from avoidance of backlash plus a safety margin and ranging from 0.05 to 0.1 mm Corresponding concentricity accuracies of preferably less than 0.02 mm for machine sizes in the center distance range of about 100 mm to about 500 mm (below which the value is correspondingly smaller, above it larger)
3. (3) Protection of the sensitive components, in particular the rotor bearing (especially on the outlet side) and the two drive units by the described purge gas system ( 30 and 31 )
4. (4) as far as possible * ° * regardless of the external conditions of use in the sense that the R718 positive displacement compressor system adapts itself to a wide variety of conditions. * ° * as much as possible so that there are practically no restrictions on the conditions of use.
5. (5) Intelligent guidance via the Control Unit ( 15 ) in particular the cooling fluid flows and in accordance with PIRSA such that the R718 Verdrängerverdichtersystem has the lowest energy consumption at each operating point, that works with maximum efficiency and at the same time fulfills the aforementioned tasks.

• ❶ Gehäuse-Wärmebilanz-Führung
• ❷ 2z-Rotor-Wärmebilanz-Führung
• ❸ 3z-Rotor-Wärmebilanz-Führung
• ❹ Einspritzung zur Verdampfungskühlung während des Verdichtungsvorgangs
• ❺ Motorenkühlung

The necessary ability for accomplishing these tasks according to the invention in terms of intelligence lies in the control unit ( 15 ). Both the design and the operation according to the invention are to be designed such that the tasks mentioned above are always reliably fulfilled. To fulfill these tasks, the following regulatory variables are available according to the invention:

• ❶ Housing heat balance guide
• ❷ 2z rotor heat balance guide
• ❸ 3z rotor heat balance guide
• ❹ Injection for evaporative cooling during the compression process
• ❺ engine cooling

The speed adjustment is done by FUs ( 2.4 and 3.4 ) via the electronic motor pair spindle rotor synchronization with the FU-CU ( 16 ) in conjunction with the Control Unit ( 15 ).

VET stands for compressor end temperature = that is the temperature at the gas outlet of the compressor

Injection cooling ❹ provides the main cooling component during compression, whereas workspace component cooling esp. To compensate for different thermal expansions per workspace component and / or to protect sensitive components (especially the rotor bearing and the drive motors) of the control unit ( 15 ), by doing so in the algorithm of the control unit ( 15 ) is deposited.

Evaporator ( 7 ) with the (low) pressure p ₁ and the temperature t ₀ before the positive-displacement compressor condenser ( 8th ) with the (higher) pressure p ₂ and the temperature t _c after the positive displacement compressor machine, the refrigerant R-718 of p ₁ on p ₂ compressed, with the refrigerant R-718 the temperature increase of t ₀ on t _c experiences.

Basic explanation:

The cooling water "Kü" generally supplies the heat Q̇ _off from the condenser ( 8th ), while the cold water "Ka" in the evaporator ( 7 ) the heat Q̇ _ent is withdrawn from the Verdrängerverdichtersystem.

und den einzelnen Kühlfluidströmen ❶ ❷ ❸ ❹ und ❺ zur Erfüllung der o. gen. Aufgaben.The cooling medium (abbreviation: "KM") refers to the water coming from the evaporator ( 7 ) as cooling fluid flow regulated by the control unit ( 15 ) in the cooling medium distribution ( 26 ) is diverted to split into mainstream

and the individual cooling fluid flows ❶ ❷ ❸ ❹ and ❺ to fulfill the above-mentioned tasks.

1. (1) Der Wärmehaushalt für das Verdichtergehäuse (1) wird erfindungsgemäß als sogen. „Gehäuse-Wärmebilanz-Führung“ über den Zwischenwassermantel (5) applikationsspezifisch von der Control-Unit (15) wahlweise eingestellt gemäß:
   1. a) über äußeres Kühlwasser „Kü“ im Zwischenwassermantel (5) gekühlt, wenn die Control-Unit (15) anhand der tatsächlich vorliegenden Temperaturwerte (insbes. für „Kü“) im Vergleich zu den in der Control-Unit (15) hinterlegten Datenbank feststellt, dass die applikationsspezifisch verfügbaren Kühlwasser-Temperaturen günstig (meist im Sinne von niedrig genug) für den Gehäuse-Wärmehaushalt sind, um zwischen Verdichtergehäuse (1) und Spindelrotorpaar (2 und 3) eine Spielsituation einzustellen, die einerseits den Crash (als Spielaufzehrung) sicher zu vermeiden und andererseits für die optimale Effizienz der Verdichtung hinsichtlich der inneren Spaltleckage zu sorgen, konkret: Die Spaltwerte zur Crash-Vermeidung liegen etwa im Bereich von 0,03 bis 0,05 mm, dazu kommt ein Sicherheitsaufschlag (beispielsweise wegen Rundlaufabweichungen) von ungefähr 30% bis 50%, so dass sich die unteren Spaltwerte ergeben, als ΔSp.u bezeichnet. Die oberen Spaltwerte ΔSp.o sollten vorzugsweise nicht mehr als Faktor 2 größer als ΔSp.u sein. Durch unterschiedliches thermisches Dehnungsverhalten der Arbeitsraum-Bauteile (also im Wesentlichen das Gehäuse und das Rotorpaar) muss das über die von der Control-Unit (15) regulierten Kühlfluidströme (9) als sogen. Wärmehaushaltmanagement nun applikationsspezifisch die tatsächlichen Spaltwerte zwischen ΔSp.u und ΔSp.o halten.
   2. b) Wenn die applikationsspezifisch verfügbaren Kühlwasser-Temperaturen ungünstig (zumeist im Sinne von zu hoch) für den Gehäuse-Wärmehaushalt sind, dann sorgt die Control-Unit (15) über den Kühlfluidstrom 9.1 (als ❶ dargestellt) beispielsweise mittels Regulierorgan (26) und einfacher Kühlrohrschlange (6) insbes. im Auslass-Bereich für die Abführung der aufsteigenden Wärme im Zwischenwassermantel (5), wobei aufsteigend im Sinne der Erstreckung in Rotorlängsachsrichtung abhängig von der Konvektion im Zwischenwassermantel als Zwischenmediumträger und Ausgleich gegen zu hoher Temperatur-Differenzen.
2. (2) unlimited durch interne Kühlung im Betrieb unabhängig von äußeren Bdgn. sich selbst einstellend, also bei 5°C Umgebungs-Bdgn. wie auch bei 60°C = keine Grenzangaben mehr nötig = selbsttätig wird die Kondensator-Temperatur hochgefahren und die innere Kühlung passt sich selbständig an also keine Anforderungen mehr zur max. zulässigen Kühlwasser-Temperatur = erfindungsgemäß ist nunmehr alles machbar
3. (3) insbes. auch die E-Motore sind dank anpassbarer Intensiv-Kühlung prakt. beliebig überlastbar
4. (4) Zwischenwassermantel (5) am Verdichtergehäuse (1) mit Isolationsmantel (20) zum Kondensator (8)
5. (5) Verdichter mit offenem Einlass (11) und Auslass (12), es gibt keine seitlichen Abschluss-Gehäuseteile („Deckel“) mehr, es ist kein klassisch autarker Verdichter mehr sondern eine offene Maschine
6. (6) Kühlmechanismen von der Control-Unit als sogen. „Arbeitsraumbauteile-Wärmemanagement“ intelligent abgezweigt und verteilt gemäß:
   • 
     ist der Hauptsrom zur Erfüllung der eigentlichen Aufgabe zwischen Wärmeaufnahme im Verdampfer und Wärmeabgabe im Kondensator
   • ❶ Kühlung für das Verdichtergehäuse, vzw als Verdampfer-Kühlung über Zwischenwassermantel auch nur so viel, dass die über die minimierte Rotorkühlung ❷ und ❸ sich ergebenden Spaltwerte in einem gewählten Bereich bleiben, z.B. vzw. innerhalb von ± 25%
   • ❷ Bauteile-Kühlung für den 2-zähnigen Spindelrotor → minimiert(!) primär zum Schutz der Lager
   • ❸ Bauteile-Kühlung für den 3-zähnigen Spindelrotor → minimiert(!) primär zum Schutz der Lager
   • ❹ Kühlung per Kühlmedium-Einspritzung → trägt als wichtigste Größe die Hauptlast, also > 80%
   • ❺ Kühlung für jeden Antriebsmotor→ nur zur Rettung der Funktion (überwacht & geführt von den Motor-Thermo-Elementen, vzw. in den Motorwicklungen)
7. (7) Bauteile-Kühlung ❶ und ❷ und ❸ zwecks Umsetzung von 2 Haupt-Anforderungen:
   • → Beherrschung der Spiele-Situation, um unterschiedliche thermische Dehnungen kompensieren zu können, wobei die Spielwerte vorzugsweise innerhalb von etwa ± 25% bleiben sollten.
   • → k₀ -Betrieb sowie minimale Fördervolumenströme sicher und dauerhaft beherrschen
   • → Vermeidung zu hoher Temperaturen bei kritischen Bauteilen, insbes. die Auslass-seitige Lager
8. (8) Einspritzung ❹ als der Haupt-Kühlmechanismus mittels Verdampfung während der Verdichtung
   • ► Ziel: feiner Nebel als mögl. große Oberfläche für effiziente Verdampfung als Wärmeabführung während der Verdichtung
   • ► Schleuderscheiben mit rauer Oberfläche mit Endneigung zur Vermeidung von Rinnsalen, für mögl. gleichmäßige Verteilung
   • ► Schleuderscheibe mit äußerer Rinne ggfls. mit radialen Abspritzbohrungen, um den Schlupf zu vermindern
   • ► Zuführung zur Schleuderscheibe oder ggfls. als Abspritzbohrung im Fußgrund über Doppelrohr oder über den Stützarm für den Ansauglagerträger
   • ► Einspritzung statt Schleuderscheibe über Bohrungen im Fußgrund am Einlass nehmen (wohl eher nicht)
   • ► Einspritzung als Regulierung der tatsächlichen inneren Verdichtung nehmen: Die verdampfende Flüssigkeit führt zu starkem Volumen-Anstieg in der Arbeitskammer mit entspr. Druck-Anstieg
9. (9) Achsabstand zwischen den Spindelrotoren am Einlass (11) vorzugsweise um mind. 10% größer als am Auslass (12)
10. (10) Anpassung des inneren Volumenverhältnisses Π_iv über Vakuum-taugliche Steuerkugeln (10), vzw. Gewichts-belastet von der Gasdruckdifferenz beiseite gedrückt und auch Schwerkraft-bedingt auf einer unter dem Winkel γ_R angeschrägten (vzw. Elastomer-)Lauframpe (10.R) wieder zurücklaufend, wenn Δp wieder fällt und ausgeführt
    • • während der Rotorlänge (beispielhaft in 2 dargestellt)
    • • sowie an der Endplatte (12) als Steuerscheibe (beispielhaft in 1 dargestellt)
11. (11) Auslass-Endplatte als Steuerscheibe (12) über Schälscheiben zur idealen Spieleinstellung für den stirnseitigen Spalt zwischen dem Rotorende und der Endplatte für jeden Spindelrotor individuell
12. (12) Aufwand zur iV-Anpassung (z.B. per Steuerkugeln) kann applikationsspezifisch drastisch reduziert werden, indem die jeweiligen Druckwerte sowohl am Kondensator als auch am Verdampfer bei gleichzeitiger Volumenstrom-Anpassung so eingestellt werden, dass das Druckverhältnis dieser beiden Druckwerte mit dem inneren Volumenverhältnis Π_iv des Verdichters derart übereinstimmt, dass eine Über- oder Unterverdichtung in akzeptablen Grenzen gehalten vermieden wird gemäß PIRSA = Pressure-InnerRatio-Speed-Adaption = Druck-InneresVolumenverhältnis-Drehzahl-Anpassung
13. (13) Steigungsverlauf über den Zahnflankenversatz Δk_vs(z) unterschiedlich zwischen rechter und linker Zahnflanke zur Maximierung der Querschnittsfläche in jedem Stirnschnitt insbes. im Ansaugbereich: Indem bei einem rechtssteigend ausgeführten 2z-Spindelrotor die rechte Zahnflanke gegenüber der linken Zahnflanke den beispielhaft dargestellten Verlauf hat, verringert sich bei dem 2z-Spindelrotor dessen Zahnbreite zwecks Maximierung der Stirnschnitt-Arbeitskammer-Schöpfflächen im Ansaugbereich als erfindungsgemäßer Zahnflankenversatz der Flanken zueinander bezeichnet
14. (14) zylindrische Spindelrotor-Innenkühlung kann auf den letzten Bereich beschränkt werden, also nicht über die ganze Rotorlänge (mit entsprechendem Anstieg der Fußgrund-Wandstärke am Einlass)
15. (15) dargestellt ist die Maximal-Version (quasi der „Mercedes“), indem alle Kühlmechanismen realisiert sind - es wird aber auch eine abgespeckte Version (quasi der „VW“) geben, indem vorzugsweise / beispielsweise auf die Bauteile-Kühlung verzichtet wird und die Temperaturen während der Verdichtung nur über die Einspritzkühlung eingestellt wird, d.h.: obige Ziele nur noch eingeschränkt erfüllbar, weil das für einige Applikationen ausreichend ist.
16. (16) Antriebsmotore auf der Einlass-Seite (wegen Bauraum sowie als Temperatur-Schutz mit Überlast-Option)
17. (17) k₀ -Drehzahl-Messung (als Eigen-Diagnose zur Feststellung von Veränderungen, z.B. Belagbildung etc.)
18. (18) CFK-Zwischenträger (17) am 2-zähnigen Spindelrotor zur Gewichts-Reduzierung, insbesondere das Massenträgheitsmoment beim Hochfahren (beschleunigen) bei zugleich hoher Biegesteifigkeit
19. (19) Ausführung zum Purgen über die Zwischenräume mit Bypass-Bohrung je Spindelrotor-Lagerung
20. (20) umlaufende Überlauf-Rinne im Verdampfer und Abfluss an der tiefsten Stelle für die Betriebsmodi entsprechend 14 als Alternative zum geschlossenen Kreis mit dem Steigrohr (19)
21. (21) Mischbatterie und Mischstrecke als Option zur gezielten Temperaturen-Einstellung
22. (22) vorzugsweise mit CO2-Kaskade für tiefere Temperaturen

„vzw“ steht für „vorzugsweise“The following points are cited for better understanding: (also as repetition)

1. (1) The heat balance for the compressor housing ( 1 ) According to the invention as so-called. "Housing heat balance guide" over the intermediate water jacket ( 5 ) application-specific from the Control Unit ( 15 ) optionally set according to:
   1. a) via external cooling water "Kü" in the intermediate water jacket ( 5 ) cooled when the control unit ( 15 ) based on the actual temperature values (esp. for "Kü") compared to those in the Control Unit ( 15 ) that the application-specific available cooling water temperatures are favorable (usually in the sense of low enough) for the housing heat balance to be between compressor housing ( 1 ) and spindle rotor pair ( 2 and 3 ) to set a game situation on the one hand to avoid the crash (as Spielaufzehrung) and on the other hand to ensure the optimum efficiency of compression in terms of inner gap leakage, specifically: The gap values for crash avoidance are approximately in the range of 0.03 to 0, 05 mm, plus a safety impact (for example due to concentricity deviations) of approximately 30% to 50%, so that the lower gap values result, designated as ΔSp.u. The upper gap values ΔSp.o should preferably no longer be a factor 2 be greater than ΔSp.u. Due to different thermal expansion behavior of the working space components (ie essentially the housing and the rotor pair), this must be done via the control unit ( 15 ) regulated cooling fluid streams ( 9 ) as so-called. Heat Management now application specific hold the actual gap values between ΔSp.u and ΔSp.o.
   2. b) If the application-specific available cooling water temperatures are unfavorable (usually in the sense of too high) for the housing heat balance, then the Control Unit ( 15 ) over the cooling fluid flow 9.1 (shown as ❶), for example by means of regulating organ ( 26 ) and simple cooling coil ( 6 ) esp. In the outlet area for the removal of the rising heat in the intermediate water jacket ( 5 ), with ascending in the sense of extension in Rotorlängsachsrichtung depending on the convection in the intermediate water jacket as intermediate medium carrier and compensation for excessive temperature differences.
2. (2) unlimited due to internal cooling in operation independent of external Bdgn. self-adjusting, so at 5 ° C ambient Bdgn. as well as at 60 ° C = no limit information necessary = automatically the capacitor temperature is increased and the internal cooling adapts itself automatically so no more requirements for max. permissible cooling water temperature = according to the invention now is all feasible
3. (3) esp. Also the e-motors are thanks to customizable intensive cooling practical arbitrarily overloaded
4. (4) intermediate water jacket ( 5 ) on the compressor housing ( 1 ) with insulation jacket ( 20 ) to the capacitor ( 8th )
5. (5) Compressor with open inlet ( 11 ) and outlet ( 12 ), there is no side closure housing parts ("cover") more, it is not a classically self-sufficient compressor but an open machine
6. (6) cooling mechanisms of the control unit as so-called. "Workspace components-thermal management" intelligently branched off and distributed according to:
   • 
     is the main power to fulfill the actual task between heat absorption in the evaporator and heat dissipation in the condenser
   • ❶ cooling for the compressor housing, vzw as evaporator cooling via intermediate water jacket only so much that the gap values resulting from the minimized rotor cooling ❷ and in remain within a selected range, eg vzw. within ± 25%
   • ❷ Component cooling for the 2 - toothed spindle rotor → minimizes (!) primarily to protect the bearings
   • ❸ Component cooling for the 3 - toothed spindle rotor → minimizes (!) primarily to protect the bearings
   • ❹ Cooling by cooling medium injection → is the main variable, the main load, ie> 80%
   • ❺ cooling for each drive motor → only to save the function (monitored & guided by the motor-thermo-elements, vzw. In the motor windings)
7. (7) component cooling ❶ and ❷ and ❸ for the implementation of 2 Main requirements:
   • → mastering the game situation to compensate for different thermal expansions, with the game values preferably staying within about ± 25%.
   • → k ₀ Operation and minimum volume flow rates safely and permanently
   • → Avoidance of high temperatures in critical components, especially the exhaust side bearings
8. (8) Injection ❹ as the main cooling mechanism by evaporation during compression
   • ► Target: fine mist as possible. large surface area for efficient evaporation as heat dissipation during compaction
   • ► Sliding discs with rough surface with end inclination to avoid run-offs, for possible. even distribution
   • ► Slinger with outer gutter if necessary. with radial spray holes to reduce slippage
   • ► Feed to the centrifugal disc or if necessary. as Abspritzbohrung in the footwell via double pipe or on the support arm for the Ansauglagerträger
   • ► Inject injection instead of centrifugal disc over holes in the bottom of the foot at the inlet (probably not)
   • ► Injection as regulation of the actual internal compression: The vaporizing liquid leads to a strong increase in volume in the working chamber with corresponding increase in pressure
9. (9) Center distance between the spindle rotors at the inlet ( 11 ) preferably at least 10% larger than at the outlet ( 12 )
10. (10) adjustment of the internal volume ratio Π _iv via vacuum-compatible control balls ( 10 ), vzw. Weight-loaded pushed by the gas pressure difference aside and also due to gravity on a tapered at the angle γ _R (or elastomer) running ramp ( 10.R) running back again when Δp falls again and executed
    • • during rotor length (example in 2 shown)
    • • as well as on the end plate ( 12 ) as a control disk (exemplified in 1 shown)
11. (11) outlet end plate as control disk ( 12 ) via peeling discs for the ideal clearance adjustment for the frontal gap between the rotor end and the end plate for each spindle rotor individually
12. (12) Expenditure on iV adaptation (eg by means of control balls) can be drastically reduced in the application-specific manner by adjusting the respective pressure values both on the condenser and on the evaporator with simultaneous volumetric flow adjustment such that the pressure ratio of these two pressure values coincides with the internal volume ratio Π _{iv of} the compressor is such that over- or under-compression is kept within acceptable limits, according to PIRSA = Pressure-InnerRatio-Speed-Adaptation = pressure-to-internal-volume-ratio-speed-adaptation
13. (13) Gradient progression over the tooth flank offset Δk _vs (z) different between right and left tooth flank to maximize the cross-sectional area in each incision cut esp. In the intake: By the right flank opposite the left flank has the course shown by way of example in a rechtszend designed 2z spindle rotor is reduced in the 2z-spindle rotor whose tooth width in order to maximize the cutting edge working chamber-Schöpfflächen in the intake area referred to as inventive tooth flank offset of the flanks to each other
14. (14) cylindrical spindle rotor internal cooling can be limited to the last range, ie not over the entire rotor length (with a corresponding increase in Fußgrund wall thickness at the inlet)
15. (15) shown is the maximum version (quasi the "Mercedes"), by all cooling mechanisms are realized - but it will also give a slimmed-down version (quasi the "VW") by preferably / is omitted, for example, the component cooling and the temperatures during the compression is set only by the injection cooling, ie: the above goals can only be fulfilled to a limited extent, because this is sufficient for some applications.
16. (16) Drive motors on the inlet side (due to installation space and as temperature protection with overload option)
17. (17) k ₀ -Speed measurement (as self-diagnosis to detect changes, eg deposit formation, etc.)
18. (18) CFRP intermediate carrier ( 17 ) at the 2 - toothed spindle rotor for weight reduction, in particular the moment of inertia during startup (accelerate) at the same time high flexural rigidity
19. (19) Execution for purge via the interstices with bypass hole per spindle rotor bearing
20. (20) circumferential overflow channel in the evaporator and drain at the lowest point for the operating modes accordingly 14 as an alternative to the closed circle with the riser ( 19 )
21. (21) Mixer and mixing section as an option for targeted temperature adjustment
22. (22) preferably with CO2 cascade for lower temperatures

"Vzw" stands for "preferably"

list of figures

• 1 : 1 shows an example of a longitudinal section through the inventive R718 Verdrängerverdichtersystem ( 42 ) when standing. The compressor machine ( 41 ) separates evaporator ( 7 ) with the lower pressure values p ₁ = p ₀ and temperature t ₀ from the capacitor ( 8th ) with the higher values for pressure p ₂ = p _C and temperature t _C , each with enveloping and the vacuum-holding housing pot ( 28 and 29 ), preferably cylindrical and on the compressor housing extension ( 1.P) according to 5 firmly. The usual vacuum pump to ensure the negative pressure in the illustrated R718 Verdrängerverdichtersystem ( 42 ) is not marked, but well known and will be according to 4 during purge preferably via the protective gas discharge ( 31 ) according to 4 used. For more detailed illustration is in the 3 the inlet area with evaporator ( 7 ) of this presentation and in 4 the outlet area with condenser ( 8th ) shown enlarged. About peeling discs ( 18 ) are on the inlet side of the positions of the spindle rotor units ( 39 and 40 according to 13 ) adjusted in Rotorlängsachsrichtung the important rotor head housing gap values. Likewise, on the outlet side, peeling disks ( 18 ) the front-side spindle rotor gap values to the outlet control disk ( 12 ).
• 2 : As an exemplary sectional view regarding. 1 perpendicular to the axis of the housing pot ( 28 ) approximately halfway along the rotor axis with a view towards the outlet ( 12 ) as a cylindrical cooling system cross section for the R718 positive displacement compressor system with control balls ( 10 ) both in the rotor longitudinal axis direction (the control balls are shown cut and hatched accordingly) and as a plan view of the outlet control disk ( 12 ) simply as circular control ball openings in 1 at the outlet ( 12 ) are shown again cut and hatched. In addition, at the outlet control disc ( 12 ) the end outlet openings ( 27 ) with the control edges ( 27.S) good to see.
• 3 : As an exemplary representation of the intake from 1 with representation of the respective cooling fluid flows ❶ and ❷ and ❸ and ❹ and ❺ with
  
  as cycle medium R718 main stream to fulfill the core task of heat transfer. In addition to the various possibilities for cooling fluid flow supply different versions for heat transfer in the evaporator ( 7 ) at the same time (practically realized separately), for example by the refrigerant R-718 via the overflow channel ( 37 ) over a sufficiently large area to drain ( 37.a) flows OR via separate heat exchanger surfaces ( 38 ), for example as inserted heat exchanger pipe system ( 38 ) at the bottom of the housing pot ( 29 ) to the heat transfer shown Q̇ _ent to ensure from the evaporation process. In order to minimize undesired heat transfer, various isolation approaches ( 29.i) represented, for example, by insulating layer (left side in 3 ) or by evacuated space (right side in 3 ).
• 4 : As an exemplary representation of the outlet area 1 with representation for housing cooling over intermediate water jacket ( 5 ) with cooling coil ( 6 ), as well as control balls ( 10 ) in the outlet control disk ( 12 ) and purge gas device by inert gas supply ( 30 ) and execution ( 31 ) via buffer space ( 13 ) via the aforementioned vacuum pump suction for the desired negative pressure in Verdrängerverdichtersystem, also exemplified with the Regulierorgan ( 26 ) to the application-specific of the Control Unit ( 15 ) regulated division of the cooling fluid streams ❶ and ❷ and ❸ and ❹ and ❺ (referred to as "KM-TS.Δ") and with
  
  as circulatory medium R718 main stream (as "KM-HS").
• 5 : As an exemplary 3D representation of the compressor housing ( 1 ) with separation between evaporator space and condenser space via the preferably cylindrical separating plate ( 1.P) , in addition with the attached preferably three bearing carrier support arms ( 24 ) per bearing carrier ( 25 ). In this illustration, the principle of the "open" compressor becomes clear, because in the housing only the two spindle rotation units ( 39 and 40 ), and the compressor machine ( 41 ) is practically finished, without own frontal end parts (therefore "open" compressor)
• 6 : Illustrated is the feeder ( 23.1 ) of injection refrigerant ❹ to the centrifugal disc ( 22 ) via a bearing carrier support arm ( 24 ) in the compressor inlet area ( 11 ) increases 1 by, for example, via a small tube, the cooling fluid flow ❹ onto the centrifugal disk ( 22 ), where then über then evenly distributed by centrifugal forces in the conveying gas flow at the inlet ( 11 ) arrives at optimum speed profile with respect to the spindle rotor.
• 7 : As an exemplary representation of the centrifugal disc ( 22 ) preferably rough rough surface for slip reduction and better cooling fluid flow O distribution, with diameter Øa.s and height h and angle γ _S significantly affect the cooling fluid flow ❹-Abspritzung of the centrifugal disc and are executed application specific.
• 8th : As an exemplary representation of the control ball ( 10 For the adjustment of the internal volume ratios to different temperature strokes with the corresponding pressure differences, wherein the angle γ _A and γ _R with respect to the gravitational direction g preferably by gravity by the pressure difference Ap on the control ball between the respective working chamber pressure and the outlet pressure rolling on the Ramp ( 10.R) , in which case a special material is not necessarily necessary, and when the pressure difference decreases, preferably automatically rewinding due to gravitational forces.
• 9 : Exemplary representation of the spindle rotor profile pairing, wherein the non-parallel axes of rotation actually three-dimensional task is shown simplistic in the plane. As a cross-section through the pair of spindle rotors the Kopfkreisbogenwinkel be.2K (z) showing the tooth flank offset .DELTA.k _vs (z) as a different z (φ) -Verlauf for right and left profile edge per tooth results, and with the respective μ-value to each spindle rotor via the rotor head circles with the a (z) run to the rotor axis distance.
• 10 When determining the rotor profile pairing, the following functional characteristics are shown as an example for the crossing angle α = 15 ° between the rotor axes of rotation at a rotor profile length of L = 376 mm, showing the tooth flank offset Δk _vs (z) over the Δ.be.2K (z) -Verlauf with respect to the pitch curve m (z) in the rotor longitudinal axis z map, where as abscissa always this z-step is selected, ie the range of values: 0 ≤ z ≤ L where the outlet ( 12 ) at z = 0 and the inlet ( 11 ) at z = L
  • 10 .1: [only exemplary values] The assignment between the rotation angle run parameter φ for the range 0 ° ≤ φ ≤ 1320 ° and the z position as z (φ) function yields the slope curve m (φ) via the known equation: $$\boxed{\text{m}\left(\mathrm{\phi }\right)=2\mathrm{\pi }\cdot \frac{\text{dz}\left(\mathrm{\phi }\right)}{\text{d}\mathrm{\phi }}}$$
    
    Plotted over the longitudinal axis of the rotor, the gradient progression m (z) is then shown, which starts at 28 mm at z = 0 mm, then increases rapidly to a pronounced maximum area in front of the inlet (FIG. 11 ), wherein the slope at z = L again drops sharply to 78 mm.
  • 10 .2: [only exemplary values] The tooth height h (z) in the rotor longitudinal axis direction results for each axial distance a (z) according to the crossing angle over the intermeshing spindle rotor heads, the rotor head radii values following the respective μ values then following equations: $$\boxed{{\text{R}}_{\text{2K}}\left(\text{z}\right)={\mathrm{\mu }}_2\left(\text{z}\right)\cdot \text{a}\left(\text{z}\right)}\text{and}\boxed{{\text{R}}_{\text{3K}}\left(\text{z}\right)={\mathrm{\mu }}_2\left(\text{z}\right)\cdot \text{a}\left(\text{z}\right)}\text{such as}\boxed{\text{H}\left(\text{z}\right)=\left({\mathrm{\mu }}_2\left(\text{z}\right)+{\mathrm{\mu }}_3\left(\text{z}\right)-1\right)\cdot \text{a}\left(\text{z}\right)}$$
    
    The lead in 10 .2 shown in FIG 1 shown cylindrical rotor receptacle to the evaporator cooling at each spindle rotor esp. In k ₀ To enable operation.
  • 10 .3: [example values only] As a continuation of 10 .2 are to the shown μ-values for the angle of the elbow be.2K (z) am 2 - toothed spindle rotor two versions shown:
    • • In the event that there is no tooth flank offset between right and left flank side, the dashed-dotted be.2K.stu (z) run results for the head bend angle, decreasing steadily from 65 ° at z = 0 to 53 ° z = L wanders.
    • The inventive be.2K.em (z) run starts at z = 0, for example, even at 65 °, but then shows a significantly different course in that there is a minimum in the last third of the rotor length inlet side, after which it then rapid rises to 70 ° at z = L.
  • 10 .4: [example values only] As a continuation of 10 .3 is now the slope m (z) according to 10 .1 is registered and clearly recognizable (as described) the opposite course between be.2K.em (z) and m (z)
  • 10 .5: [example values only] In addition to 10 .3 and 10.4, the difference between be.2K.em (z) and be.2K.stu (z) is additionally mapped as Δ.be.2K (z) in conjunction with the gradient m (z), so that the inventive concept for tooth flank offset Δk _vs (z) becomes clear between left and right tread side.
• 11 : As an exemplary representation are for the rotor assembly as 11 .1 and 11 .2 and 11 .3 three different pairs of spindle rotors, which in their outer / connection geometry to the same compressor housing ( 1 ), but at least matching the same housing blank, the following description applies:
  • 11 Fig. 1 shows by way of example a spindle rotor pair with high pumping speed at a moderate number of stages for applications in which it is less about the compressibility but more about high volume flow.
  • 11 .2 shows by way of example a spindle rotor pair with medium pumping speed at medium number of stages for applications without a pronounced emphasis, ie a more general orientation.
  • 11 .3 shows by way of example the spindle rotor pair with lower pumping speed at very high number of stages for applications in which high compressibility is more important than volume flow.
• 12 :
  • 12 .1: Exemplary representation for an alternative design to the outlet control disk ( 12 ), in which on control balls ( 10 ) can be omitted by the exhaust control disk rotatable as ( 12.s) with the pivot bearings ( 12.g) as well as the exit slot ( 12.s) at the 2 toothed spindle rotor end is executed.
  • 12 .2: Exemplary representation for the execution of the rotatable outlet control disk ( 12.d) with the exit slot ( 12.s) as well as additional side outlet notches ( 12.k) so that the ejecting last working chamber does not close again when the minimum internal compression ratio is set. These notches are needed because the exit slot ( 12.s) not too much of the circle may occupy, otherwise the factor by which the internal compression can be increased decreases. When the maximum internal compression ratio is set, the outlet notches ( 12.k) above the chamber, which is without outlet control disc ( 12.d) just open. The outlet notches ( 12.k) are then removed from the outlet plate which terminates the 3z rotor and the compressor housing ( 1 ) closed sideways. Shortly before the last working chamber has completely emptied, the compressor housing ( 1 ) is removed laterally and the 3z rotor is open.
• 13 : Illustrated are the finished and fully balanced spindle rotor rotation units ( 39 and 40 ), without further intervention via the peeling discs ( 18 ) in the compressor housing ( 1 ) are used unchanged for exact gap adjustment and thus the open compressor machine ( 41 ) form.
• 14 : Exemplary are shown 3 Operating modes for operating the R718 Positive Displacement Compressor system for various cooling water ("ü") and cold water ("a") temperature levels that are controlled by the Control Unit (PIRSA) as "Pressure-InnerRatio-Speed-Adaptation". 15 ) as described application-specific optimally adjusted.

LIST OF REFERENCE NUMBERS

1.

Compressor housing preferably at the same time with Ø-separating plate ( 1.P) between evaporators ( 7 ) and capacitor ( 8th ) at inlet side by at least 15% -igigment greater distance of the spindle rotor mounting holes as the outlet side, these bore axes are preferably cutting (ie with zero pitch) or even crossing (or skewed) are executed.

Second

Spindle rotor, preferably with 2 -zähnigem gas delivery external thread, short "2z rotor" called, preferably made of an aluminum alloy with good thermal conductivity (preferably above 150 W / m / K), rotationally fixed on support points on a steel shaft ( 2.1 ) with cylindrical evaporator cooling bore ( 2.2 ) and is directly driven on the inlet side by its own drive motor ( 2.3 ) controlled with its own frequency converter ( 2.4 ), referred to as "FU.2", and with FU-Control-Unit as "FU-CU" ( 16 ) by electronic motor pair spindle rotor synchronization

Third

Spindle rotor, preferably with 3 -zähnigem gas delivery external thread, short "3z rotor" called, preferably made of an aluminum alloy with good thermal conductivity (preferably above 150 W / m / K), rotationally fixed on support points on a steel shaft ( 3.1 ) with cylindrical evaporator cooling bore ( 3.2 ) and is directly driven on the inlet side by its own drive motor ( 3.3 ) controlled with its own frequency converter ( 3.4 ), called "FU.3", and with FU-Control-Unit as "FU-CU" ( 16 ) by electronic motor pair spindle rotor synchronization

4th

Bearing for each spindle rotor, mounted on both sides, whereby the inlet side is preferably designed as a fixed bearing ( 4.1 ) for axial and radial forces and outlet side as preferably spring-loaded floating bearing ( 4.2 )

5th

Intermediate water jacket for heat balance regulation for the compressor housing ( 1 ) with external heat insulation ( 20 ) to the surrounding capacitor ( 8th )

6th

Cooling coil in the intermediate water jacket, which is preferably narrower on the outlet side and to the evaporator ( 7 ) ends

7th

Evaporator with the (low) pressure p ₁ = p ₀ and the temperature t ₀ in front of the compressor machine ( 41 )

8th.

Capacitor with the (higher) pressure p ₂ = p _C and the temperature t _C after the compressor machine ( 41 ), the refrigerant R-718 from the pressure p ₁ on p ₂ condensed, with the refrigerant R-718 fundamentally the temperature increase of t ₀ on t _C experiences.

9th

respective cooling fluid flows to the full extent of the control unit ( 15 ) regulated guidance of the heat balances of the working space components, thus housing and rotor pair, as well as to the compression process according to:

9.1

Cooling fluid flow (shown as ❶) to the intermediate water jacket ( 5 ) via cooling coil ( 6 )

9.2

Cooling fluid flow (shown as ❷) to 2z rotor ( 2 ) via evaporator cooling bore ( 2.2 )

9.3

Cooling fluid flow (shown as ❸) to 3z rotor ( 3 ) via evaporator cooling bore ( 3.2 )

9.4

Cooling fluid flow (shown as ❹) for injection cooling via centrifugal disc ( 22 )

9.5

Coolant fluid flow (shown as ❺) for cooling each drive motor

the circulation medium R718 main flow is shown to fulfill the core task of heat transfer (eg as a heat pump or in the refrigeration process).

10th

Control ball suitable for vacuum adjustment of the internal volume ratio Π _iv for different operating points to avoid efficiency-reducing over- or under-compression both in the rotor longitudinal axis and each control disk ( 12 ) according to the desired application area with ramp ( 10.R) inclined with angle γ _R opposite to the direction of gravity "g" according to 8th

11th

Delivery gas inlet as an open collecting space for the pumped medium with the gas pressure p ₀ (simplifying pressure losses in the lines are initially neglected)

12th

Delivery gas outlet as a control disk per spindle rotor with defined outlet openings for the pumped medium at the gas pressure p _C (simplifying pressure losses in the lines are initially neglected)

13th

neutral collection / buffer space per working space shaft passage with reduced gas pressure compared to the system pressure, preferably e.g. produced by a vacuum / vacuum pump, as "purge suction" the rotor bearings ggfls. To be able to purge = protect so by inert gas, this inert gas is supplied from the outside of each bearing, these bearings then passes through a bypass hole and is sucked off again at this collection / buffer space.

14th

Synchronization toothing as mechanical fallback protection for electronic motor pair spindle rotor synchronization, for example in the event of power failure after regenerative operation

15th

Control unit CU as a control and regulation unit with evaluation of the respective current measured values and based output of the control signals for intelligent operation of the spindle compressor in preferably stored in CU memory links and data as well as learning interdependencies between each incoming measured values and the gap values according to previous simulation, verification and current experience, the control unit is connected to FU-CU ( 24 ) as well as the user side with the process control technology for its application system as well as factory control iS of "Industrie-4.0"

16th

FU-Control-Unit, called "FU-CU", for both frequency inverters FU.2 ( 2.4 ) and FU.3 ( 3.4 ), whereby FU-CU directly with the control unit ( 15 ) exchanges the data for the spindle compressor operation.

17th

Intermediate carrier on 2 - toothed spindle rotor ( 2 ) with low density (less than 2.5 g / cm ³ ) but high flexural stiffness, preferably as a fiber composite material, such as CFRP vacuum suitable

18th

Spacer / spacer discs, preferably as so-called. "Slicing discs" designed for individual fixation of the respective spindle rotor in the rotor longitudinal axis direction for targeted gap value adjustment as a Δ2.1 value at the 2z rotor ( 2 ) or as Δ3.1 value at the 3z rotor ( 3 )

19th

Pressure reducing organ in the closed internal circuit, for example, by exploiting the geodetic height difference in a water column, so use of gravity to reduce pressure

20th

Heat insulation for the intermediate water jacket ( 5 )

21st

directed support for the control balls

22nd

Centrifugal disc (preferably with rough / coarse surface) for feeding and fine distribution of the cooling fluid flow into the intake area ( 11 ) of the compressor according to ❹ as injection cooling

23rd

Supply of the cooling fluid flow ❹ to the centrifugal disc ( 22 ), this feed being carried out as desired:

23.1

Supply of cooling fluid flow ❹ via a cantilever arm ( 24 ) the bearing carrier ( 25 )

23.2

Supplying the cooling fluid flow ❹ via the central bore in each rotor carrier shaft ( 2.1 respectively. 3.1 )

24th

Cantilever of the bearing carrier, preferably 3 Piece per bearing carrier ( 25 ), fluidically favorable

25th

Bearing carrier for receiving the rotor bearings ( 4 ), on the outlet side at the same time the frontal chamber boundary

26th

Regulatory organ for the control unit ( 15 ) guided division of the cooling fluid streams ( 9 )

27th

End outlet openings with control edge ( 27.S) per rotor after the control balls ( 10 ) from a value previously specified for the application to the internal volume ratio Π _iv

28th

Vacuum-compatible condenser housing pot on the housing ∅ separation plate ( 1.P) attached and sealed lying on vertical, the condenser housing pot is placed on top

29th

Vacuum-compatible evaporator housing pot preferably on the housing ∅ separation plate ( 1.P) attached with insulation ( 29.i , shown as cross-hatching or as a vacuum space) to ensure efficient Q̇ _ent heat balance, in vertical operation, the evaporator housing pot is attached at the bottom

30th

Inert gas supply (so-called "purges") for the protection of the bearings ( 4 ) as well as if necessary. the drive units such that these areas to be protected always have a slightly higher pressure (eg a few mbar differential pressure, eg 3 to 10 mbar) than the direct R718 steam environment; as inert / protective gas, normal air will suffice in most applications, but it is also possible, for example, to choose nitrogen

31st

Protective gas discharge generated by a separate vacuum backing pump, which preferably also provides for the vacuum system pressure. With this protective gas discharge, a certain R718 water vapor partial stream is sucked off via the working space shaft seal, so that this R718 loss must be returned as water. As a seal to mitigate this R718 water vapor loss substream, increase the flow resistance of the working space shaft seal, for example, via a brush seal

32nd

Bearing bypass hole to prevent gas flow through the bearing ( 4 )

33rd

Supply of the cooling fluid flow to the rotor internal cooling for the respective spindle rotor as:

33.1

Feed tube in the central bore of each spindle rotor carrier shaft

33.2

Supply of cooling fluid flow ❷ to 2z rotor internal cooling via feed tube ( 33.1 )

33.3

Supply of cooling fluid flow ❸ to 3z rotor internal cooling via feed tube ( 33.1 )

34th

Retaining bush in central carrier shaft bore to prevent the cooling fluid from flowing away

35th

Symbol for the compressor according to the invention 1

36th

heat exchangers

36.ü

Heat exchanger on the cooling water side

36.a

Heat exchanger on the cold water side

37th

circulating overflow channel in the evaporator for supplied evaporating water with drain ( 37.a) in operation according to 13 , in which case this effluent water to cooling fluid flow ( 9 ) applies

38th

Heat exchanger (eg as a pipe system) for heat transfer Ȯ _ent inside the evaporator ( 7 )

39th

Spindle rotor rotation unit for 3 - toothed spindle rotor system

40th

Spindle rotor rotation unit for 2 - toothed spindle rotor system

41st

(entire) compressor machine as open 2 -Shaft rotary displacement machine

42nd

(entire) R718 positive displacement compressor system

Claims (10)

Spindle compressor as a 2-shaft rotary displacement machine for conveying and compressing gaseous fluids, preferably water vapor, with a pair of spindle rotors (2 and 3) in a compressor housing (1) characterized in that the R718 Verdrängerverdichtersystem (42) of the said elements as the described open compressor machine (41) is executed with electronic motor pair spindle rotor synchronization, wherein the compressor machine (41) between the evaporator (7) and capacitor (8) is arranged and separates both from each other. Spindle compressor in the R718 positive displacement compressor system Claim 1 , characterized in that the two drive motors (2.3 and 3.3) are arranged on the side of the conveying gas inlet (11) and fully in the space of the evaporator (7) protrude for sufficient dissipation of the power losses preferably via the cooling fluid flow ❺ (9.5) accordingly their burden. Spindle compressor in the R718 Verdrängerverdichtersystem according to any one of the preceding claims, characterized in that the described heat balance management of the designated "unlimited" operation for all operating / working states, in particular in k ₀ operation, the R718 Verdrängerverdichtersystems (42) is achieved in which the sensitive components such as rotor bearings and drive units are protected by means of said purge system via protective gas feed (30) and protective gas discharge (31). Spindle compressor in R718 Verdrängerverdichtersystem according to any one of the preceding claims, characterized in that at least one centrifugal disc (22), but preferably one Centrifugal disc (22) on each spindle rotor (2 or 3), on the conveying gas inlet side (11) introduces the injection cooling amount ❹ (9.4) in the conveying gas flow. Spindle compressor in the R718 Verdrängerverdichtersystem according to any one of the preceding claims, characterized in that the Verdrängerprofilflanken both spindle rotors (2 and 3) with the tooth flank offset .DELTA.k _vs (z) between right and left flank side is executed, which is exemplified by the Δ.be. 2K (z) -Verlauf with respect to the pitch curve m (z) in the rotor longitudinal axis z represent and produce can. Spindle compressor in R718 Verdrängerverdichtersystem according to any one of the preceding claims, characterized in that control balls (10) in the described embodiment, the application specific targeted adaptation of the internal compression ratios. Spindle compressor in the R718 Verdrängerverdichtersystem according to any one of the preceding claims, characterized in that the 2-toothed spindle rotor (2) with intermediate carrier (17) is provided for weight reduction, in particular for a lower moment of inertia during startup (or braking) at the same time high bending stiffness, for example made of vacuum-compatible fiber composite material, eg as CFRP material. Spindle compressor in R718 Verdrängerverdichtersystem according to any one of the preceding claims, characterized in that the rotor assembly described, exemplified in 11 shown, for easy adaptation of the properties of the R718 Verdrängerverdichtersystems (42) to application-specific different requirements built and used. Spindle compressor in the R718 Verdrängerverdichtersystem according to any one of the preceding claims, characterized in that the sub-compression is damped with the described outlet-gap-iV adjustment. Spindle compressor in R718 Verdrängerverdichtersystem according to any one of the preceding claims, characterized in that the above procedure according to PIRSA as "Pressure-InnerRatio-speed adaptation" on said operating parameters, the efficiency of the R718 Verdrängerverdichtersystems (42) in each working / operating point is optimized by means of control unit (15).

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