STEAM COMPRESSOR COMPRISING A DRY POSITIVE-DISPLACEMENT UNIT AS A SPINDLE COMPRESSOR

Abstract

The invention relates to a spindle compressor designed as a twin-shaft rotary displacement machine for delivering and compressing flow media, particularly steam. It comprises a pair of spindle rotors in a compressor housing (1) comprising an inlet collecting space (11) and an outlet collecting space (12). The centre distance of the pair of spindle rotors is at least 10% longer on the inlet-side end than on the outlet-side end. Each of the two spindle rotors (2, 3) is driven by an electric motor (18, 19), and an electronic synchronisation controls the electric motors (18, 19) such that the spindle rotors (2, 3) rotate in a contact-free manner.

Claims

1. A spindle compressor as a 2-shaft rotary positive-displacement machine, working without operating fluid in the working space, for conveying and compressing gaseous conveyed media, preferably steam, comprising a spindle rotor pair in a compressor housing (1) which has an inlet collection chamber (11) and an outlet collection chamber (12), characterised in that the centre distance of the spindle rotor pair at the inlet-side end is at least 10% greater than at the outlet-side end, in that each of the two spindle rotors (2, 3) is driven by an electric motor (18, 19), and an electronic synchronisation controls the electric motors (18, 19), and in that the spindle rotors (2, 3) rotate contact-free.

2. The spindle compressor according to claim 1, characterised in that one spindle rotor (2) has two teeth, in that the other spindle rotor (3) has three teeth, and in that the electronic synchronisation is a 2 to 3 synchronisation.

3. The spindle compressor according to claim 1, characterised in that each spindle rotor (2 or 3) has an internal cooling means, which preferably is embodied as a cylindrical evaporator cooling bore (6) of radius RC2 on the 2-toothed spindle rotor (2) or of radius RC3 on the 3-toothed spindle rotor (3).

4. The spindle compressor according to claim 3, characterised in that the evaporator cooling bore (6) has an inner structure with at least one of the following features, preferably more than one: a) at least one cooling fluid guide groove (16), preferably with precise (deviation <1%) observance of the R.sub.C value, in particular with a.1) groove base faces with angles of inclination (z) with 170(z)180 as f(z) and/or a.2) the outlet region has a larger surface for heat transfer than the inlet region, b) cooling fluid distribution overflow grooves (17) c) support points (7) for non-rotational support on the corresponding carrier shaft (4 or 5) d) steam outlet (14) in the inlet chamber (11).

5. The spindle compressor according to claim 1, characterised in that each spindle rotor system is embodied with the rotary unit (40) ready-assembled and balanced, and in that separator plates (26) are preferably provided for the final setting of the play between rotor heads and housing.

6. The spindle compressor according to claim 1, characterised in that at least one vibration sensor (39) is provided and is connected to a control unit (25), and in that in the control unit (25) the supplied amount of the cooling fluid flow (9) is limited to the amount corresponding to a maximisation of the overall efficacy.

7. The spindle compressor according to claim 2, characterised in that the critical bending speed of the 2-toothed spindle rotor is approximately (with a tolerance of preferably less than 30%) 1.5 times higher than the critical bending speed of the 3-toothed spindle rotor (3).

8. The spindle compressor according to claim 1, characterised in that the crossing angle alpha between the two spindle rotor axes of rotation in combination with the corresponding (z) value in the rotor longitudinal axis direction is such that, for each rotor, a cylindrical evaporator cooling bore (6) with minimal (that is to say appropriate for the particular tooth height in respect of material strength) wall thicknesses w is created on the supporting root-base body (32) (for example in accordance with the aforementioned position descriptions of E, S, V and L) under simultaneous consideration of the (preferably) blowhole-free profiling of the gas-conveying external thread (31) and critical bending speed appropriate for the specific rotor spindle and implementation of the inner volume ratio as iV value (as explained), wherein the gas-conveying external thread (31) is formed in the inlet region as a 2-toothed spindle rotor (2) preferably with cylindrical flattened portion (27).

9. The spindle compressor according to claim 1, characterised in that the thermal situation for the working space components is regulated in an application-specific manner as basic step (as explained) during the component heat dissipation during operation to maintain the play values between avoidance of play reduction and excessive differences in the play values (as explained) and as FCT stage (as explained) during the component heat dissipation, to improve efficacy as diverted cooling fluid flow as separate cooling water flow via delayed evaporation with cooling fluid injection (33) into the compressor working space, preferably in the region of the inlet collection chamber (11), which is all regulated and controlled by the control unit (25).

10. The spindle compressor according to claim 1, characterised in that each spindle rotor (2, 3) consists of an aluminium alloy and is pressed on to a steel shaft (4, 5) at the support points (7) for conjoint rotation, and in that the gas-conveying external thread (31) is only then produced and the spindle rotor (2, 3) has an inner structure that is already completed.

11. The spindle compressor according to claim 1, characterised in that the inner volume ratio is adapted to the current operating conditions via additional partial outlet openings (15).

12. The spindle compressor according to claim 1, characterised in that a steam outlet (14) directly to the inlet is provided.

13. The spindle compressor according claim 1, characterised in that a cylindrical flattened portion (27) is provided at the inlet of the 2-toothed spindle rotor, in particular in that the gas-conveying external thread (31) in the case of the 2-toothed spindle rotor (2) has the cylindrical flattened portion (27) in the inlet region.

14. The spindle compressor according claim 1, characterised in that the 2-toothed spindle rotor (2) is provided with an intermediate support, whereby a weight reduction, in particular also for a lower moment of inertia during start-up (or braking) alongside high flexural rigidity, is preferably achieved for example from fibre-composite material suitable for vacuum, for example in the form of a CFRP material.

15. The spindle compressor according to claim 1, characterised in that at least one cooling fluid feed (9.2 and 9.3) is provided, and in that each spindle rotor has a cylindrical evaporator cooling bore (6), which is connected to the cooling fluid feed (9.2 and 9.3).

16. The spindle compressor according to claim 1, characterised in that each drive has a hollow shaft, in that the cooling fluid feed (9.2 and 9.3) to the cylindrical evaporator cooling bore (6) of a drive is provided through this hollow shaft, and in that the bearings (10) are preferably formed as durable bearings, in particular grease-lubricated-for life hybrid bearings, all-ceramic bearings, or also magnetic bearings.

Description

[0301] In the figures, instead of a subscript, merely a dot is inserted as index, so that for example R.F2 means R.sub.F2 and thus here denotes the root radius on the 2-toothed spindle rotor, wherein:

TABLE-US-00001 F stands for profile root K stands for profile head C stands for cooling WK stands for pitch circle 2 stands for the 2-tooth spindle rotor (2) 3 stands for the 3-toothed spindle rotor (3

[0302] FIG. 1 shows, by way of example, a 2-toothed spindle rotor (2) in longitudinal section with rotor geometry according to the invention and with cylindrical evaporator cooling bore (6) according to the invention and adapted positive-displacement profile root-base wall thickness w for the load-bearing root-base body (32) on the basis of the example of the 2t rotor with detail of the steam outlet (14) over a plurality of (balanced with the necessary cross-section ) transverse bores from the cylindrical evaporator cooling bore (6) with the radii values which are as follows:

R.sub.w2<R.sub.D2<R.sub.C2

for the preferably blowhole-free profile pairing, the gas-conveying external thread (31) on the 2-toothed spindle rotor is located above the pitch circle line (37). As is known, the drive motor (18) consists of a motor rotor (mounted on the carrier shaft 4 for conjoint rotation) and a motor stator assembly with the electrical stator motor windings (shown by squared hatching),
optional: extraction to the vacuum pump (29) starts at the neutral chambers (13) of the working space shaft bushings, in order to protect the bearings from the conveyed medium as necessary

[0303] FIG. 2 shows, by way of example, a cooling circuit with diversion of to cooling fluid (9) from the circuit, with cooling fluid injection (33) into the compressor working space per working point, targeted adjustment of the inner compressor volume ratio as iV value by additional partial outlet openings (15), with steam outlet (14) per working space component, i.e. housing (1) and rotor pair (2 and 3), shown in the inlet space (11)

the expansion valve, which is also shown, in the case of steam as the circulation medium, is preferably replaced via the simple height difference with the use of gravity as a hydrostatic pressure difference (the present illustration would then have to be adapted to the direction of the force of gravity).

[0304] The control unit (25) receives and processes various signals regarding the current operating requirements, the entire circulation system and in particular also from the compressor according to the invention, in order in particular to adjust the compressor components for each working point via the regulation members (38), such that the requirements are met in the best possible wayonly with the control unit (25) can the system work reliably and efficiently (in practice a New Intelligence). [0305] Referring to PCT/EP2015/062376=similar, but now improved by said inventive features to meet the requirements of steam.

[0306] FIG. 3 shows, by way of example, a spindle rotor pair end-face section with an adaptation of the (z) values in the rotor longitudinal axis direction simplified as a projection in a common plane, because the rotor axes of rotation are at the angle alpha to each other and ought to be shown three-dimensionally, for the various positions E, S, V and L of FIG. 5

where the following is true for the (z) values:

[00005]$\begin{array}{c}{R}_{K.Math..Math.2}\left(z\right)={}_2\left(z\right).Math.a\left(z\right)\end{array}.Math..Math.\text{and:}.Math..Math.\begin{array}{c}{R}_{K.Math..Math.3}\left(z\right)={}_3\left(z\right).Math.a\left(z\right)\end{array}$

[0307] Adaptation of the (z) values for the rotor pairing according to the invention, preferably as 3:2 pairing to fulfil the following 3 core tasks: [0308] maximising the nominal pumping capacity (based on the rotor pair cross-sectional area, achieve the greatest possible scoop area) [0309] with blowhole-free rotor pairing (minimise internal leakage) [0310] with optimum use of the critical bending speed at each spindle rotor, specific to their respective speeds

[0311] Design: For each of the 2t rotor and the 3t rotor with different cooling bore values R.sub.C2 and R.sub.C3 wherein the supporting steel shafts have not been shown for simplicity, and

different head strength distribution, since the root angle .sub.F2>90, so that the tooth cross-section of the 2-toothed spindle rotor (2) is slightly slimmer, without dropping below a minimum head width b.sub.K2 below (for example 5 mm).

[0312] This happens in such a way that the critical bending speeds per rotor (i.e. for 2t and 3t) match, so that the following is achieved for the spindle rotor pair: [0313] The rotor pairing is without a blowhole, and therefore the internal leakage is reduced. [0314] Based on the illustrated rotor pair cross-section, this design achieves significantly more scoop area and thus an increased pumping capacity relative to the cross-section, which is sought for steam compression. [0315] Accordingly, the 2-toothed spindle rotor has the larger cooling bore for heat dissipation during compression, so that the component heat balance is improved in respect of heat absorption and heat dissipation. [0316] The 2t rotor has a speed 1.5 times higher than the 3t rotor and accordingly it is embodied in accordance with the invention in such a way that this 2-toothed spindle rotor achieves the more rigid shaft thanks to R.sub.F2>R.sub.F3 at reduced (by means of .sub.0>90) mass, which is favourable for the increase of the critical bending speed, because the 2-toothed spindle rotor also has to rotate faster and accordingly has to be designed in accordance with the invention with the higher critical bending speed limit. [0317] Accordingly, the slower 3t rotor has a lower bending critical speed due to the lower bending stiffness, for which reason it also rotates slower. [0318] According to the invention, the rotor pair is now designed in such a way that the critical bending speed at the 2t rotor is 1.5 times higher than the critical bending speed at the 3t rotor, wherein the following is sought:

[00006]$\begin{array}{c}{}_{\underset{2.Math.\text{-}.Math.\mathrm{rotor}}{\mathrm{critical}}}=1.5.Math.{}_{\underset{3.Math.\text{-}.Math.\mathrm{rotor}}{\mathrm{critical}}}\end{array}.Math..Math.\text{with}.Math..Math.\begin{array}{c}{}_{\underset{\mathrm{generally}}{\mathrm{critical}}}=\sqrt{\frac{c}{m}}\end{array}$

bending critical speed generally as the square root of stiffness over mass

[0319] FIG. 4 shows an example as shown in FIG. 1 but for the 3t rotor with external profile conveying thread area below the pitch circle line (37), displacement profile area=where there is arranged the outer conveying thread (31) with profile teeth and tooth gap areas, which form the various working chambers as a series connection between the inlet and outlet and below the pitch circle line (37) ensure the blow hole-free compression.

[0320] FIG. 5 shows by way of example: rotors from FIG. 1 and FIG. 3 paired to show the overall rotor geometry and indicating the crossing angle alpha and the spindle rotor pairing with the engagement lens area engaging centrally with one another

[0321] FIG. 6 shows, by way of example, a total of 4 CAD illustrations, showing: [0322] 6a) a compressor housing (1) formed as a pot housing: [0323] i.e. outlet-side closed bottom side and internal processing of the working space from the open inlet side [0324] 6b) Rotation unit: [0325] each spindle rotor with carrier shaft, bearing, drive motor and measurement system as a completely assembled and balanced unit (40), ready for mounting and henceforth unchanged, shown here only with the example of the 2-toothed spindle rotor, although the same applies for the 3-toothed spindle rotor, wherein the cylindrical flattened portion (27) at the 2t rotor inlet is not shown. [0326] 6c) assembly and play adjustment: [0327] shown for both via separator plates (26) for the important rotor head play relative to the housing, by way of example as a detail for the head play 2.1 between 2-toothed spindle rotor head and housing. The final clearance adjustment between rotor heads and the housing is performed via separator plates (26), this being illustrated by way of example as 2.1 in FIG. 6c for the 2-toothed spindle rotor head. [0328] 6d) finished machine: [0329] Both rotation units mounted in the pot housing plus frequency converter (22 and 23) per motor incl. FU control unit (24), which communicates with the control unit (25) for continuous data exchange, which FU control unit in turn is connected to the user process controller. [0330] The motor windings of the two drive motors (18 and 19) are protected against the conveyed medium for example by vacuum-proof potting of the motor stator winding assemblies or also by gap pots between the motor stator and motor rotor, etc.

[0331] The rotor internal geometry according to FIGS. 1 to 4 with the cylindrical evaporator cooling bore has not been included in FIG. 6, since this embodiment, as described, instead of applying for the described evaporator component cooling via a cylindrical evaporator cooling bore (6) according to FIG. 2, now applies for the option with separate cooling water flow as cooling water operation according to the industrial property right PCT/EP2016/077063, wherein in this embodiment a cylindrical internal rotor cooling is not required, because the internal rotor cooling shown in FIG. 6 is suffice.

[0332] This FIG. 6 shows: [0333] good and reliable balancing for the rotary units, in particular for the desired high speeds implemented in the case of steam to about 350 m/sec as max. rotor head speed. [0334] easy installation as a modular system, since different rotor pair variants in the same housing geometry [0335] targeted play adjustment via the separator plates (26) in order to be able to compensate for the particular tolerance situation (because all production parts have deviations/dimensional differences within certain tolerances) caused by unavoidable manufacturing tolerances individually (as precisely as possible for these various components). [0336] electron. synchronisation via (18) and (19) as drive for each rotation unit [0337] and with C as a control unit for the intelligent cooling of the components (as described above)

[0338] FIG. 7 shows by way of example: operating/working points as a basis (Excel) for the prior art=for turbo, improvement by the present invention by the higher T with heat dissipation for t.sub.C [0339] more T is desired for heat release below t.sub.C [0340] this cannot be done by one of today's turbos (already working with 2 stages) [0341] there must be a positive-displacement machine, which creates the p/p pressure ratio [0342] at the same time the machine must imperatively be formed as an absolute/complete dry-running machine due to steam

[0343] FIG. 8 shows, by way of example, an illustration of the compression process in a pressure-enthalpy graph in the case of steam compression, showing the improvement due to the intensive evaporator heat dissipation during compression [0344] prior art is shown as the dot-and-dash line (with labelling) [0345] improvement according to the invention is shown as dashed line (with labelling) compressing from to

Purpose of the Presentation:

[0346] Prior art represented by turbo, which must work in two stages with intermediate cooling, as compared to the improvement of the invention, here referred to as HydroCom (abbreviated to HC)

Explanation of the Prior Art:

[0347] In order to isentropically compress.sup.(Carnot) from 8 mbar (to =4 C.) to 48 mbar (t.sub.c=32 C.), intermediate cooling is indispensable for a 2-stage turbo because already isentropically from 8 mbar to 48 mbar there would already be a temperature rise of from 4 C. to approx. 200 C., without intermediate cooling.

Improvement According to the Invention:

[0348] Because of the enormous p/p pressure conditions with high isentropic exponent, the best-possible heat dissipation during compression must be ensured, which would otherwise lead to a fatally high (in the sense of increased compressor power) rise in compression temperatures, and therefore in accordance with FIG. 8 compression is performed practically almost at the dew line (i.e. better than isentropically), wherein the rotor pair cooling effort for to somewhat worsens the overall efficiency in refrigeration technology due to the diverted cooling fluid flow (9.2 and 9.3).

[0349] Thus, HC fulfils a stronger requirement profile according to FIG. 7 in that, in accordance with the invention, improved HC works from 7 mbar=2 C. to 96 mbar=45 C., thanks to efficient heat dissipation during compression.

[0350] FIG. 9 shows, by way of example: an Excel design table with example values for the parameter values for the positions E, S, V and L, stated by way of example, in the rotor longitudinal axis direction for the spindle rotor pair with individual values per spindle rotor, the indicated power specifications being only quite rough and constituting provisional reference values. Of course, both the selection of the named positions and the selection of other parameter values for the particular application-specific requirement profile are imperative.

[0351] Therefore, it should again be emphasised at this juncture that this is merely an example, showing only one of many possible design options for the rotor pair design according to the invention for demonstration purposes only.

[0352] For some applications, it may be favourable that the cylindrical evaporator cooling bore (6) is designed in a multi-stepped cylindrical form, as terraces so to speak, with the overflow edge as shown by way of example in FIG. 1.

[0353] Where reference is made here generally to cooling fluid, what is meant here is the R718 cooling fluid known from the field of refrigeration, which is naturally compressed at the chosen negative pressure as steam in the positive-displacement machine according to the invention, or in liquid form as cooling fluid (9) for component cooling by evaporation.

[0354] Terms such as substantially, preferably, and the like, and also possibly, which are understood to be imprecise, are to be understood such that a deviation by 5%, preferably 2%, and in particular 1% from the normal value is possible. The applicant reserves the right to combine any features and also sub-features from the claims and/or any features and also sub-features from a sentence in the description in any manner with other features, sub-features or partial features, even beyond the features of independent claims.

[0355] In the different figures, parts that are equivalent with respect to their function are always provided with the same reference signs, so that they are generally described only once.

[0356] Since the lowest temperatures in the case of steam are above 0 C., the combination with the refrigerant R744 as CO.sub.2 (as a 2-stage solution, also known as a cascade) is advantageous for lower temperature values (for example for deep freezing).

[0357] The invention relates to steam compression for refrigeration, air conditioning and heat pump technology, both for clockwise and anticlockwise (Carnot) cyclic processes. In order to improve the efficacy and operating behaviour at the same time with a greater pressure range, the present invention proposes a dry 2-shaft positive-displacement machine as spindle compressor, the spindle rotors (2 and 3) of which have a rotor pair centre distance which on the inlet side (11) is at least 10% greater than on the outlet side (12), and being driven by electronic motor pair (18+19)-spindle rotor (2+3) synchronisation, and each spindle rotor being provided with internal cooling, wherein the crossing angle alpha between the two rotor axes of rotation is formed in combination with the corresponding (z) value in the rotor longitudinal axis direction in such a way that a preferably cylindrical evaporator cooling bore (6) with minimal wall thickness w at the supporting root-base body (32) is formed for each spindle rotor under simultaneous consideration of the (preferably) blowhole-free profiling of the gas-conveying external thread (31) and critical bending speed appropriate for the specific spindle rotor and implementation of the inner volume ratio as iV value, wherein the inner volume ratio is adjusted during operation via additional partial output openings (15) and the gas-conveying external thread (31) in the case of a 2-toothed spindle rotor (2) is preferably formed with a cylindrical flattened portion (27) in the inlet region.

LIST OF REFERENCE SIGNS

[0358] 1. Compressor housing with outer cooling areas and inlet-side greater distance of the spindle rotor receiving holes than on the outlet side, these bore axes being preferably intersecting (i.e. with perpendicular distance zero) or also crossing (or skewed), with external cooling fins for a cooling fluid flow rate (9.1) managed by control unit (25), preferably with cooling fluid flow, for example according to (9.1a) and (9.1b), in some sections in the rotor longitudinal axis, wherein for larger rotor lengths (for example >500 mm) a plurality of cooling fluid flow-through sections are formed on the compressor housing, and the compressor housing preferably is embodied as a so-called pot housing according to FIG. 6a. [0359] 2. Spindle rotor, preferably with 2-toothed gas-conveying external thread (31), called a 2t rotor for short, preferably made of an aluminium alloy with good thermal conductivity (preferably above 150 W/m/K), fixed for conjoint rotation via support points (7) on a steel shaft (4) and inside having a cylindrical evaporator cooling bore (6) with radius R.sub.C2. [0360] 3. Spindle rotor, preferably with 3-toothed gas-conveying external thread (31), called a 3t rotor for short, preferably made of an aluminium alloy with good thermal conductivity (preferably above 150 W/m/K), fixed for conjoint rotation via support points (7) on a steel shaft (5) and having inside a cylindrical evaporator cooling bore (6) with radius R.sub.C3. [0361] 4. 2t-rotor carrier shaft, connected to the 2t rotor for conjoint rotation at radius R.sub.W2 (preferably pressed on) with central cooling fluid supply bore (4.a), preferably integrally and at the same time also shaft for the 2t drive motor (18) [0362] 5. 3t rotor carrier shaft, connected to the 3t rotor for conjoint rotation at radius R.sub.W3 (preferably pressed on) with central cooling fluid supply bore (5.a), preferably integrally and at the same time also shaft for the 3t drive motor (19) [0363] 6. Cylindrical evaporator cooling bore with radius R.sub.C and length L.sub.C for the corresponding spindle rotor, preferably with cooling fluid guide grooves (16), cooling fluid distributor overflow grooves (17) and support points (7) [0364] 7. Support points as a rotationally fixed contact between spindle rotors (2 and 3) and carrier shafts (4 and 5). [0365] 8. Synchronisation toothing for the spindle rotor pair, also rotating in the case of electronic synchronisation as fallback transmission for emergency situations, for example power failure, wherein the motors then automatically switch to generative operation and only at the end (own power generation is no longer enough) does the transmission prevent the spindle rotor contact. [0366] As a fallback transmission, no lubricating oil is required, wherein this toothing is realised with increased overlap ratio (i.e. larger toothing bevel angle) so that the profile overlap can be reduced by decreasing the tooth heights for smaller sliding motions in the tooth engagement to reduce friction and hence wear, wherein the tooth flanks preferably still receive a dry-running coating as protection. [0367] 9. Cooling fluid flow for cooling the compressor working space components, i.e. rotor pair and housing, either diverted from the circulation medium (34) according to the example in FIG. 2 or as a separate cooling fluid flow shown in FIG. 6d generally, wherein, for example the following is true: [0368] 9.1 Cooling fluid flow to the compressor housing, for greater rotor lengths (for example >500 mm) divisible into: [0369] 9.1a cooling fluid flow through a portion of the compressor housing (for example housing outlet side) [0370] 9.1b cooling fluid flow through another portion of the compressor housing (for example central area) [0371] 9.2 cooling fluid flow to the 2t rotor [0372] 9.3 cooling fluid flow to the 3t rotor [0373] 10. Spindle rotor fixed bearing for receiving the gas pressure axial forces and for exact fixing of each spindle rotor in the longitudinal axis direction [0374] 11. Conveyed gas inlet collecting space for the conveyed medium with the gas pressure p.sub.0 (for simplification, pressure losses in the lines are initially ignored) [0375] 12. Delivery gas outlet collecting space for the conveyed medium with the gas pressure p.sub.C (for simplification, pressure losses in the lines are initially ignored) [0376] 13. Neutral collection/buffer space per working space shaft passage with reduced gas pressure with respect to the system pressure, preferably for example generated by negative pressure/vacuum pump. [0377] 14. Steam outlet via several transverse bores after a step with radius R.sub.D2 or R.sub.D3 per rotor [0378] 15. Additional partial outlet openings as diverted conveyed medium outlet partial gas flow with a regulating member (pressure difference valve) for adjusting the internal volume ratio [0379] 16. Cooling fluid guide grooves with the radius R.sub.C per cylindrical evaporator cooling bore (6) with groove base surfaces at an angle of inclination , which is preferably 170180, and the cooling fluid guide grooves as a thread with the greatest possible pitch=as in (31) [0380] 17. Cooling fluid distributor overflow grooves (with undersized cross-section) preferably in the groove bottom of (16) [0381] 18a. 2t drive motor as a direct drive for the 2t rotor, preferably embodied as a synchronous motor [0382] 19. 3t drive motor as a direct drive for the 3t rotor, preferably embodied as a synchronous motor [0383] 20 Rotary encoder for measuring the exact rotary angular position of the motor 2t rotor carrier shaft (4) [0384] 21. Rotary encoder for measuring the exact rotary angular position of the motor 3t rotor carrier shaft (5) [0385] 22. Frequency converter, referred to as FU.2, for the 2t drive motor (18) [0386] 23. Frequency converter, referred to as FU.3, for the 3t drive motor (19) [0387] 24. FU control unit, designated as FU-CU, for both frequency converters FU.2 (22) and FU.3 (23), wherein the FU-CU directly exchanges the operating data with the control unit (25). [0388] 25. Control unit CU as a control and regulation unit with evaluation of the current measured values and output, based thereon, of the regulation signals for intelligent operation of the spindle compressor with links and data preferably stored in the CU memory as well as ever-learning dependencies between the incoming measured values and the gap values according to previous simulation, verification and ongoing 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 in the sense of Industry 4.0 [0389] 26. Distance/spacer plates, preferably embodied as separator plates for individual fixing of the spindle rotor in the rotor longitudinal axis direction for targeted gap value adjustment as 2.1 value on the 2t rotor (2) or as 3.1 value on the 3t rotor (3) [0390] 27. Cylindrical flattened portion (as cyl. dimension specification in FIG. 2) on the 2-toothed spindle rotor (2) over the radius R.sub.KE2 on its rotor inlet side [0391] 28. Circulation medium through the evaporator (35) for heat absorption (as a core task in refrigeration technology) [0392] 29. Vacuum pump for removal of foreign gases and for generation of the necessary negative pressure for the steam cycle, preferably sucking said gases into the neutral spaces (13) to protect the (rotor) bearings. [0393] 30. Water reservoir to compensate for water losses [0394] 31. Gas-conveying external thread with preferably blowhole-free profile rotor pairing to perform the compressor core task, namely to transport the gaseous conveyed medium from the inlet (11) to the outlet (12) and at the same time compress it [0395] 32. Supporting root-base body with wall thickness w at each spindle rotor (2 and 3) [0396] 33. Cooling fluid injection into the working space of the compressor [0397] 34. Circulating medium through the condenser (36) for heat output (as a core task in heat pumps), circulating medium here is steam (circulating through different states), but in principle also suitable for other circulation media, for both clockwise and anticlockwise Carnot processes [0398] 35. Evaporator for the circulating medium, in which a quantity of heat is absorbed. [0399] 36. Condenser for the circulating medium, in which a quantity of heat is output. [0400] 37. Pitch circle line (abbreviation: WK) for the spindle rotor in question [0401] 38. Regulation members for selective adaptation of the volume flow rate of the cooling fluid flow (9), managed by the control unit (25) [0402] 39. Vibration sensors to determine modified residual unbalance suggestions by different amounts of cooling fluid per spindle rotor internal cooling [0403] 40. Rotation unit per spindle rotor system, each fully assembled and balanced, primarily consisting of: [0404] spindle rotor (2 and 3) [0405] carrier shaft (4 and 5) [0406] synchronisation toothing (8) [0407] bearing, with (10) as fixed bearing plus working space shaft seals, for example with (13) [0408] drive motor (18 and 19) [0409] rotary encoder measurement system (20 and 21) thus, a total of two rotation units (40) per spindle compressor