WO2018134200A1

WO2018134200A1 - Steam compressor comprising a dry positive-displacement unit as a spindle compressor

Info

Publication number: WO2018134200A1
Application number: PCT/EP2018/051005
Authority: WO
Original assignee: Steffens, Ralf
Priority date: 2017-01-17
Filing date: 2018-01-16
Publication date: 2018-07-26
Also published as: US20200386228A1; EP3571408A1; JP2020505544A; CN110520626A

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.

Description

Water vapor compressor with dry displacement machine as spindle compressor

Circular processes are preferably described according to Carnot with heat dissipation and heat absorption and a compressor as a drive for the circulation medium in the gaseous phase. Circular processes are used very frequently and have become indispensable in our daily lives. These include right- and left-rotating Carnot processes, with desired / targeted heat intake to fulfill a cooling task (in the refrigeration and air conditioning industry) or with desired / targeted heat delivery to fulfill a heating task (keyword "heat pump ") with heat exchangers for heat absorption and heat release. For the movement of the circulation medium, a drive in the form of a compressor (compressor) for the circulating medium in its gaseous phase is generally required. First, the circulation medium with its specific properties is crucial. There are now various artificial (generally chemically produced such as HFC and HFC) as well as circulating media and natural (such as ammonia, propane, propylene, isobutane, ethane) cycle media.

Non-refractory, however, water is ideal as a circulation medium because of its general availability, it is completely non-toxic, can be safely used at low pressures as water vapor and meets even the most stringent guidelines and safety regulations, is resource-friendly, environmentally friendly, low maintenance, efficient and practically without any risk potential (incombustible, non-explosive, uncritically).

The challenge is on the compressor side, because in the working pressure range of a few mbar not only enormous large volume flow quantities but also very high pressure conditions are required. This results in enormously difficult compression conditions esp. By high temperatures, especially since the isentropic exponent of water vapor in this pressure range with about 1, 327 is quite high, for comparison: Today's refrigerant here in the range of just over 1, 1 with correspondingly moderate increases in temperature in the compressor.

The task of water vapor compression is nowadays addressed by turbo compressors, but must be performed in several stages to meet the high pressure conditions with simultaneous intercooling. However, the fundamental characteristic weakness as a turbomachine allows only moderately satisfactory temperature and pressure conditions. If there were a more efficient compressor solution here, steam would be a significant advancement as a cycle medium because of its enormous benefits.

The object of the present invention is the compression of (preferably) water vapor in the known working area and pressure range, which is generally referred to as a rough vacuum, by a positive displacement machine with mastery of the respective desired pressure differences and the large p / p pressure conditions with the Displacement machine typically steep characteristic (ie pressure values on volume flow with the corresponding operating points) to accomplish, this machine must be completely dry running (no operating fluid) and should have a total efficiency for the entire system, which is better for the entire application than the Today's turbocompressors, so that the user requirements in refrigeration and heat pumps and other (Carnot) circular processes are better met, especially in terms of a larger pressure range. This object is achieved according to the invention for the compression of water vapor at pressures below atmospheric pressure (preferably between 6 mbar and 300 mbar, ie in the classic vacuum region) in the power range of less than 1 kW to well over 100 kW as refrigeration cycle power for refrigeration (ie industrial refrigeration , Commercial refrigeration and building air conditioning) or as heat pump cycle power [the required compressor power is corresponding to the so-called. "COP" ⁽ ' ^{e |)} value less than 2-shaft displacement machine according to the screw compressor principle with a gas inlet space (1 1) and a gas outlet space (12), wherein the axial distance between the spindle rotors on the gas inlet side (1 1) is greater than on the gas outlet side (12) and thus results in a crossing angle alpha, which is preferably between 3 and 25 degrees of angle and is carried out so that the features described below are met:

The features of the invention are:

1) electronic synchronization by each spindle rotor (2 or 3) is driven by its own drive motor (18 or 19), each drive motor its own FU (22 or 23), each with its own measuring system (20 or 21 ) For detecting the respective rotational angular position and a drive control unit (24), which ensures that these drive motors (18 and 19) via their own frequency converter (22 or 23) are driven at a corresponding speed such that the Spindle rotor pair (ie 2 and 3) can work without contact to each other.

The cooling fluid supply (9.2 or 9.3) to the respective cylindrical evaporator cooling bore (6) of each rotor is then additionally by the hollow shaft of the respective drive, the bearings (10) then preferably as fat-lubricated life hybrid bearings or full ceramic bearing (or Even as a magnetic bearing) are executed. ) cylindrical evaporator cooling bore (6) as a "rotating cylinder evaporator" for automatic self-cooling cooling by the water to be evaporated as a spindle rotor cooling fluid under the pressure p ₀ * and the temperature t ₀ * [these values with certain technical deviations, such as pressure drops, temp. increase due to unavoidable heat transfer] is diverted from the circuit of FIG. 2 and in the cylindrical evaporator cooling bore by rotation centrifugal forces in operation inevitably always goes exactly where it is currently most urgent for each operating point is needed, wherein the cylindrical evaporator cooling hole (preferably) has the following features as explained below:

A "rotating cylinder evaporator", as the internal cooling of the spindle rotor is designed according to the invention has the best possible heat transfer properties for the present task, because the centrifugal forces consistently the best possible heat transfer is achieved by the heavy liquid parts in the rotating cylindrical evaporator Cooling hole constantly displace the lighter gas components of the heat transfer surfaces to evaporate again immediately, so that thus get the next liquid parts for the heat transfer to the rotor material to the desired heat transfer, and also at the same time still in Rotorlängsachsrichtung thanks cylindrical-equal radii values to due to the highest evaporation, there is also the greatest need for heat removal, because there will be different power distribution for each operating point in the rotor longitudinal axis, so that with the known high evaporation enthalpy differences with less (see FIG Values in Fig. 9) cooling fluid supply highly efficient heat dissipation during compression is achieved, so that according to Fig. 8, the compressor line of [T] is advantageously steep and run for the compressor clearly better than isentropic.

The following characteristics apply to the cylindrical evaporator cooling bore:

a) Cylindrical evaporator cooling bore (6) of radius Rc along the length Lc at the spindle rotor displacement profile length LR, said cylindrical evaporator cooling bore preferably beginning between positions E and S in the inlet region and preferably via the outlet end at L, so the values for LR and Lc are comparable (approximately equal). The cylindrical evaporator cooling bore (6) is designed as a so-called "inner structure" preferably via cooling fluid guide grooves (16), cooling fluid distributor overflow grooves (17) and support points (7).

b) The cylindrical evaporator cooling bore (6) should be as exactly cylindrical as possible (ie deviations well below 1%), wherein e.g. Manufacturing tolerances in the Rc values are preferably set such that deviations tend to lead to larger Rc values in the direction of the outlet (ie in the region of the position L).

c) Spindle rotor made of an aluminum alloy is rotationally fixed with already finished "inner structure", wherein for this "internal structure" the cylindrical evaporator cooling bore (6) preferably carried out by cooling fluid guide grooves (16) with radius Rc and multiple support points (7) includes, preferably pressed on the supporting steel shaft at these support points, eg by component temperature difference, by the warmer aluminum rotor body is joined to the colder steel shaft and then leads to a firm connection in the temperature compensation, in which case only the gas delivery "external thread" (31) is made, so that the wall thickness w can be minimized in order to improve the heat conduction through shorter distances when dissipating the heat of compression.

The groove bottom of the cooling fluid guide grooves (16) is preferably designed such that the groove base surfaces are performed with inclination angles ψ (ζ), which is preferably in the range depending on the z-position in Rotorlängsachsrichtung, which is commonly referred to as z-axis

170 ° <ψ (ζ) <180 ° depending on the position z in Rotorlängsachsrichtung, so that the distribution of the cooling fluid (9) with smaller amounts of cooling fluid (because it is always only so much cooling fluid supplied that the total energy balance in the respective Operating point gives the highest efficiency) along the rotor axis is improved by the smaller filling cross-sections depending on the respective amount of cooling fluid suitable for the operating point. In this case, the cooling fluid guide grooves are preferably designed with a pitch as great as a thread, for example as in the case of the gas delivery external thread (31), in order to be able to do so to implement the task of minimizing the residual imbalance resulting from the introduction of the cooling fluid (9.2 or 9.3) into each rotor (since each fluid collects in the rotating system to the greatest possible distance from the current pivot point and thus reinforces the residual imbalance), which, for example, is very poorly met at zero slope of the cooling fluid guide grooves.

This effect of the residual imbalance amplification is inventively used simultaneously to minimize the amount of cooling fluid supplied (9.2 or 9.3) per rotor by vibration sensors (as used for example in the camp monitoring) this residual imbalance gain by an excessive amount of cooling fluid in each rotor system show, thanks to different rotor speeds (the 2z rotor always rotates 1, 5 times faster) is exactly determined in which rotor just the amount of cooling fluid is too high, so that the control unit (25) via the Regulierorgane (38) the current correct (in terms of minimum required cooling fluid) setting can make.

To compensate for deviations and to ensure the most reliable distribution of the water to be evaporated in Rotorlängsachsrichtung at the cylindrical evaporator cooling hole (6) there are in the bottom of the cooling fluid guide grooves (16) with radius Rc additionally undersized cooling fluid distributor overflow grooves (17th ) with a distance to the rotor axis of rotation which is greater than the Rc value, but at the same time have such a small cross section, so that the water contained therein over the cross section of the cooling fluid distributor overflow grooves (17) outgoing the groove bottom of the cooling fluid guide grooves (16) wetted with radius Rc.

The embodiment of the cylindrical evaporator cooling bore (6) is of course described here only by way of example with support points (7) and cooling fluid guide grooves (16) with radius Rc and with cooling fluid distributor overflow grooves (17). Of course, other embodiments are also conceivable here.

Addition of cooling fluid (9) esp. Always limited to the rotors to the minimum amount, possibly even sporadically and impulsively, both to avoid critical imbalances and to minimize the amount of diverted cooling fluid flow (9) in the sense of maximizing the total Efficiency, because this cooling fluid flow (9) the actual circulation medium (28) in the evaporator (35) is missing in the heat absorption. The cylindrical evaporator cooling bore (6) in each spindle rotor thus always receives only so much water (with a technically usual tolerance of, for example, + 1%), as is currently needed for evaporation at the respective operating point.

This minimization of the Kühlfluidstrommenge (9) is achieved for example by measurement via known and simple vibration sensors (eg for rolling bearing monitoring) to determine the degree of filling in the respective cylindrical evaporator cooling hole (6) per spindle rotor (2 or 3), because an increased Amount of water in the respective cylindrical evaporator cooling bore (6) will increase the residual imbalance in the rotating system and can, due to different speeds of the spindle rotors (the 2-toothed spindle rotor rotates by a factor of 1, 5 faster than the 3-toothed spindle rotor) as imbalance excitation associated with the respective rotation system of the 2-toothed or 3-toothed spindle rotor so that the respective amount of cooling fluid (9.2 or 9.3) is adjusted accordingly to the minimum amount. So it is supplied only as much water as is currently needed for evaporation in the current operating point.

Of course, other approaches for minimizing the cooling fluid flow amount (9) can be used. ) Steam outlet (14) from the cylindrical evaporator cooling bore (6) per spindle rotor, characterized in that the respective cylindrical evaporator cooling bore (6) with the radius Rc2 and Rc3 is executed and the steam outlet (14) via transverse bores, preferably to each other are arranged according to a paragraph over a radius RD2 or RD3, wherein RD2 or RD3 at the respective spindle rotor something (ie a few mm, eg 2 to 5 mm) is smaller than the respective Rc2 or Rc3 value of the corresponding cylindrical evaporator cooling hole (6). ) Cooling fluid injection (33) in the working space for selectively influencing the conveying gas temperatures in the working space, ie the space between the inlet (1 1) and outlet collecting space (12). ) In the case of the heat removal for the work space components, which is so significant for the dry runner, ie the pair of spindle rotors according to (2 and 3) and the compressor housing (1), two stages are to be distinguished:

A) Basic stage in component heat dissipation:

The heat dissipation for the workspace components is to ensure as a basis at all times and to ensure that game consumption (which generally leads to failure of the compressor, so-called "crash") between the work space components is reliably avoided at every operating point:

This indispensable requirement is achieved even with small amounts of cooling fluid (9), e.g. the heat dissipation for the compressor housing (1) is reduced, ie throttling of the corresponding cooling fluid flow (9.1) with minimal amounts of cooling fluid flow (9.1), so that the thermal expansion of the working space components does not jeopardize the game situation.

At the same time, at this base stage for component heat dissipation, ensure that the play values (ie, the distance values between the workspace components) remain within a certain range, ie, the minimum play values in operation is about 0.03 to 0.09 mm (depending on the size, with large machines with> 150 mm center distance above 0.05 mm), the base stage for component heat dissipation during operation should be designed so that not only the aforementioned Spielaufzehrung is safely avoided (as indispensable mandatory requirement, whereby said minimum play values receive a safety margin of about 20% to 50%), but also the play values for other operating points due to the different thermal expansion behavior of the components compared to these lower play values by a factor of 2 to max. Factor 3, which is to be ensured by this basic stage for component heat dissipation during operation and is now accessible for the first time with a dry runner via the control unit (25) (previously only feasible with wet rotors). VET stage in component heat dissipation:

(VET stands for compression end temperature, ie the temperature of the pumped liquid at the end of the compression and usually the highest gas temperature, the VET usually being detected in the outlet chamber (12).) The power requirement in the compression of a volume (and precisely this happens in the present compressor as a so-called displacement machine) is generally reduced, thereby improving the efficiency (efficiency) of the compression, if the temperature increase in this volume during the compression process can be minimized. The necessary heat dissipation during compression is known to depend on the temperature difference between the gas in this volume and the surrounding heat-dissipating surfaces of the work space components, in addition, the heat transfer coefficient (in water vapor known to be quite high values) and the heat conduction ( therefore, as the material for the spindle rotors, an aluminum alloy is preferably used). Thus, the cooler the surfaces of the working space components can be kept above the respective cooling flow, the better is the heat dissipation during compression and the lower the temperature increase of the delivery gas in the funded and compressed working chamber volumes, hence the compressor working line increasingly steeper - shown by way of example according to FIG. 8 between the points [T] and [2].

This generally achieves a reduction in the power requirement in the compression and thus improved (higher) efficiency.

Depending on the application-specific requirements and according to the corresponding parameter design (ie with respect to crossing angle, rotor length, inlet and outlet center distance, head and foot radius values per incision, pitch and number of stages and design of the so-called "internal structure" and the spindle rotor pair cross-section) for the compressor design according to the invention, the cooling fluid flow (9) for heat dissipation for the working space components can be represented by the following two approaches:

As shown by way of example in Fig. 2 as an example, the cooling fluid flow (9) is diverted from the actual circuit as a partial flow, which is considered a preferred solution because it the maximum heat dissipation with the cylindrical evaporator cooling hole (6) during compression allows. The only disadvantage is the fact that this branched cooling fluid stream (9) is withdrawn from the main stream and thus is missing in the fulfillment of the core task in refrigeration, ie the heat absorption in the evaporator (35). In heat pumps, when the heat output in the condenser (36) represents the core task, this branched cooling fluid partial flow is not lacking the circulation medium (34).

Thus, the following principle applies:

If the specific advantage of reducing the compression temperatures in the mentioned VET stage during component heat removal is greater than the disadvantage due to the reduced amount of cooling fluid (28) through the evaporator (35), then the branched cooling fluid flow (9) is cylindrical Evaporator cooling hole (6) to realize as exemplified in Fig. 2, wherein the amount of diverted cooling fluid flow (9) targeted and controlled to the respective requirements profile in the sense that in each situation and regulated by control unit (25) each branched off only as much amount as the cooling fluid flow (9), that the compressor efficiency improvement by the heat dissipation overall energy more advantageous than the disadvantage described above in the additional effort by the branched cooling fluid flow. If this approach is no longer achievable for some applications, then the "separate cooling water flow" described below applies.

Separate cooling water flow: (as shown by way of example in FIG. 6 d) If the advantage by lowering the compression temperatures in the mentioned VET stage during component heat dissipation for the respective application is weaker than the disadvantage due to the reduced amount of cooling fluid (28) the evaporator (35), then a separate cooling water flow as shown in FIG. 6 with the internal rotor cooling described in PCT / EP2016 / 077063 to be realized, which is significantly and independent of the cycle medium ensures that Spielaufzehrung between the working space components is avoided.

The benefit that the separate cooling water flow to reduce the Spielaufzehrung almost incidentally the compression temperatures lowers something is indeed included. Naturally, the respective available cooling water temperatures are decisive, so that there can be no generally valid instruction and therefore must be decided application-specific. Thus, in simple terms, the available cooling water temperatures will be different in a hot environment (countries near the equator) than in cold regions at any given time of the year (Siberia in winter).

• delayed evaporation:

If it should not come to the evaporation of the cooling fluid (9.2 or 9.3) in the cooling fluid guide grooves (16) because of the enormous acceleration values, then it is further proposed according to the invention that this cooling fluid (by heating the heat of compression now heated) by Pitot tube (such as in DE 10 2013 009 040.7 or also described in 10 2015 108 790.1) is tapped, it has a higher pressure than pc because of the high kinetic energy and consequently to a point after the compression process, for. B. in the outlet-collecting space (12), the circuit is recycled, where this liquid is then evaporated and this task specific can absorb heat again, the amount of cooling fluid is then adjusted so that the overall efficiency is improved.

In any case, the correct (in terms of efficiency and imbalance minimization) cooling fluid quantity for the respective operating / operating point of the control unit (25) is regulated, in this control unit, the corresponding data are stored (eg corresponding process simulation) as well as "trial-and-error" as self-learning process, in which the system independently tries out variations and uses the reactions (ie energy demand and power balance) to determine with which setting the highest efficiency is achieved in the respective operating point becomes. This approach can also be called "action". Therefore, it has to be decided on a case-by-case basis which of these approaches best solves the application-specific task.

Adaptation of the internal volume ratio at the respective operating point according to the invention by additional Teilauslass openings (15), preferably spring-loaded open and allow a partial gas flow from the respective working chamber in the outlet plenum (12) emerge when in this approaching the outlet working chamber of Pressure is greater than the pressure in the outlet collecting space (12), so that in the working chamber a harmful (the efficiency is deteriorated) over-compression is avoided.

The inner volume ratio (ie the quotient of the working chamber volumes between inlet and outlet) as so-called. For the most efficient (ie energy-saving) compaction, the "iV value" must be optimally adapted to the respective operating point in order to avoid damaging over- or under-compaction. In operation, the iV value can be adjusted according to the invention by means of additional partial outlet openings (15), but must first be determined via the spindle rotor pair design. The iV value is basically influenced by the following 3 variables:

• Axial distance between the rotor axes of rotation (variable due to crossing angle alpha between the rotor axes of rotation and larger at the gas inlet (1 1) than at the gas outlet (12)

• Ratio of the rotor head radii to the center distance in the respective front section as so-called.

via the equations given below at each point z in the rotor longitudinal axis direction, and moreover the foot angle YF2 is deliberately chosen in order to maximize the nominal pumping speed, the exact procedure also being described in detail below.

• Gradient in the rotor longitudinal axis direction (also determines the number of stages at the same time, ie the number of closed working chambers between the inlet and outlet), whereby the rotor length is known to be as long as possible up to the critical speed. When determining the mentioned rotor pair parameters, so the "inner volume ratio" as so-called. "iV value" (ie quotient of the] _{E in} | _ass . _{to the} [smaller] outlet working chamber volumes) corresponding to the isentropic exponent of the pumped medium, the compression process esp. With regard to the heat dissipation during the working chamber volume change (ie the compression) and the desired compression ratio (ie the ratio of outlet pressure to inlet pressure).

By way of example, this relationship is demonstrated once with reference to the values mentioned in FIG. 7:

The conveying gas (water vapor) is to be compressed, for example, from 7.0 mbar to 95.9 mbar, resulting in a compression ratio of:

95.5 divided by 7.0 = 13.7 yields.

Only in the case of isothermal compression (ie no temperature change during compression) would an internal volume ratio of 13.7 be implemented here.

Due to the increase in temperature in the working chamber during the so-called "polytropic" compression, according to the invention, starting from the present isentropic exponent for water vapor in this range of about 1.327, by the intensive heat removal during the compression via the cylindrical evaporator cooling bore (6). give an iV value of about 10 to avoid both over- and under-compression. This IV value as a change in the working chamber volumes, which results from the multiplication of the respective spindle rotor pair cross-sectional areas and the respective extent in the rotor longitudinal axis direction (generally detected via the profile gradient), is now technically realized by:

a) variation of the spindle rotor pair cross-sectional area in each end section (shown in simplified form in FIG. 3 as a planar sectional view) in Rotorlängsachsrichtung, wherein the inlet-side rotor pair cross-section is larger than the outlet side rotor pair cross-section. This cross-sectional change on the spindle rotor pair is now achieved by:

• Change of the center distance via the crossing angle alpha of the two rotor axes

• Changing the profile tooth height above the mentioned

at every z position

This change in the cross-sectional areas on the rotor pair by changing the center distance and

(See Fig. 9), wherein the respective working chamber extension is observed. In this case, it must be ensured that a cylindrical evaporator cooling bore (6), each spindle rotor having its own Rc values, results in minimum wall thickness w in the supporting base body (32) while simultaneously taking into account the different bending-critical rotational speeds, as shown by way of example in FIG 9 has been demonstrated once.

b) Change in the profile pitch (generally referred to as m) in the rotor longitudinal axis direction:

By changing the profile slope creates a so-called. "iV.m-value" (see Fig. 9 as an example), which is usually designed to be significantly larger (more than a factor of 3) greater than the "W / .a [\ - value", where the number of stages (ie the number of completed Working chambers between inlet and outlet) on the bending critical still allowable rotor length LR in compliance with the so-called. "Kammgrenze" (which tooth gap depth is still produced relative to the tooth gap width manufacturing technology) is taken into account.

Of course, these two changes act simultaneously and multiplicatively in rotor longitudinal axis in order to arrive at the desired overall iV value, in this example = 10, which is shown by way of example in FIG. 9.

It is known that the higher the heat dissipation during compression, the higher the total iV value is, the greater the reduction in the compression temperatures generally leads to an improvement in the compressor efficiency (ie efficiency increase).

Now, if the respective operating point deviates from these mentioned pressure values, the additional partial outlet openings (15) ensure the ideal adaptation to the current operating points and thus for an efficient compression process at any time.

Each spindle rotor (ie the aluminum part, which is non-rotatably mounted on the steel shaft) consists of 3 sections: a) External gas supply thread (31)

The gas delivery external thread (31) is preferably made only after the rotationally fixed connection with the respective steel shaft in order to minimize the size of the Fußgrund- wall thickness w.

b) foot floor wall thickness w (32)

to minimize resistance to heat dissipation and to maximize heat dissipation.

c) so-called "Inner structure" consisting of cylindrical. Evaporator cooling bore (6) with support points (7) and side supports which are to be sealed on the outlet side = e.g. via O-ring) and inlet-side steam outlet (14) for the cooling fluid evaporated in the cylindrical evaporator cooling bore (6) from the cooling fluid flow (9) per working space component.

By way of example, four positions in the rotor longitudinal axis direction for the description of the spindle rotor design according to the invention may be mentioned (of course, one may also take more or fewer positions, nevertheless the spindle rotor design according to the invention can be well described by using FIGS. 1 and 4 as well as FIG Gas inlet (1 1) going to the gas outlet (12) for the following positions:

In this case, the following definition applies to each position in the rotor longitudinal axis direction (usually designated as z). '^ (z) value' per spindle rotor in the profile design at each z position for the gas delivery external thread (31) of each spindle rotor:

^R _K2 ( ^z ) = μ ₂ ( ^ζ ) · ³ ( ^ζ ) | ^or - ^: | ^R _K3 ( ^z ) = μ ₃ ( ^ζ ) ³ ( ^ζ )

In addition, the foot angle γ _{Ρ2 is selected} specifically by this particular _esbe . At μ ₂ > 0.6 is performed greater than 90 °, the head cylinder width b _K2 {z) does not fall below a selected limit, eg 5 mm.

a) Position E:

on the rotor pair front end inlet side with the largest distance between the spindle rotor axes of rotation as a _E value

According to the invention with cylindrical flattening (27) on the inlet side of the 2-toothed spindle rotor (2) over the radius RKE2 in order to expand the maximum / maximum rotor head speed to a larger spindle rotor area, preferably a radii-like transition, in Figure 2 by way of example represented as "R.tan", which allows smooth transitions.

b) Position S: (can also be represented as a range over several z-values)

with the largest μ-value, preferably such that the inlet working chamber receives the largest possible volume without violating the stated boundary conditions (ie cylindrical evaporator cooling bore, wall thicknesses on the supporting base body (32), blowhole freedom, critical bending speed etc. ), wherein the μ value according to FIG. 3 and the equations given for each z position in the rotor longitudinal axis direction is specifically designed, as shown by way of example in FIG. 9.

c) Position V: (can also be represented as a range over several z-values)

according to the tooth height adapted wall thickness with reduction of the cross-sectional area in order to realize the internal compression with good heat transfer properties on the supporting Fußgrund body (32). Position L: (can also be represented as a range over a plurality of z-values), preferably as a cylindrical end, which is expediently designed to project beyond the end of the external thread into the outlet space, as shown by way of example in FIG. As an overview table, their preferred specific values are shown by way of example in FIG. 9 for these positions. The emphasis is exemplary, because both other positions and other values can be realized. The parameters mentioned in this Fig. 9 merely show a meaningful embodiment showing the "spirit" of this invention. In this case, each position can truly also be implemented as a z-range over several z-values in the rotor longitudinal axis direction and not just as a singular z-position. ) The crossing angle alpha according to FIG. 5 between the two spindle rotor axes of rotation is carried out in combination with the respective (z) value in rotor longitudinal axis direction such that each rotor has a cylindrical evaporator cooling bore (6) with minimal (ie with respect to the material Firmness to the respective tooth height) wall thickness w on the supporting Fußgrundkörper (32) is formed (for example, according to the above position descriptions of E, S, V and L) while taking into account the (preferably) blowhole-free rotor profile design of the gas delivery external thread (31) and "spindle rotor-specifically matching" (° * °) bending-critical speed according to the following point to the critical bending speed and implementation of the internal volume ratio according to the embodiment previously described.

° * ° "Spindle rotor-specific fitting" means that, according to the speed differences between the two spindle rotors, the 1, 5-fold faster rotating 2-toothed spindle rotor receives both a higher flexural rigidity and a relatively lower rotational mass, so that the critical bending speeds be exhausted by both spindle rotors alike. ) bending critical speed Attic for the two spindle rotors on their parameter interpretation (ie in terms of diameter = stiffness such that

bending-critical speed in general as root of rigidity (incl. bearing) by mass.

To achieve high speeds, each rotor system according to the invention as a rotation unit (40) running, as it is exemplified in Fig. 6b, of crucial importance, because the balance for the complete rotation unit (40), whereby the balancing quality is improved.

For it is well known that even well balanced individual parts, which are later assembled into a rotation unit which can no longer be balanced separately as a unit (which is practically always the case with state-of-the-art 2-shaft displacement machines), are then combined in their entirety to a poorer balance quality than the separately balanced and henceforth unchanged rotation unit, as shown by way of example according to the invention in Fig. 6b.

Adjusting the clearance between the spindle rotor and the compressor housing via skiving discs (26) by first fitting each spindle rotor individually in the assembly Compressor housing (1) is introduced to the contact of the spindle rotor heads with the housing bore and pulled out and fixed again on the peeling discs (26), so that the desired head gap value between the rotor head and housing exactly results, in Fig. 6c as an example as Δ2.1 shown in detail. ) The following rules must be observed for the bearings:

Since the bearings are only a single element in contact with and therefore subject to wear, the design of the bearings must be carried out with particular care. Therefore, the following rules for the bearings must be observed:

In the case of water vapor, the bearing forces (both axial and radial) are very low and the substantial load is caused by the high rotational speed, which is why in the storage technology the so-called. nd _m factor is used as a speed characteristic, ie the product of mean bearing diameter [in mm] multiplied by the speed [in rpm = 1 / min], the machine tool under the keyword "spindle storage" here provides detailed design recommendations. If this speed characteristic exceeds one million mm / min, special emphasis must be placed on speed resistance and lubrication. The rotor speed results from the maximum permissible rotor head speed below supersonic for the fluid in the work area. As a limit value for water vapor in the pressure range are given about 400 m / sec, which is why in accordance with FIG. 9 in the table with 350 m / sec a value with sufficient safety margin is selected. According to the invention, the 2-toothed spindle rotor (2) is also flattened cylindrical in the inlet area so as not to hit the rotational speed limit too early in this area, because in the outlet direction the rotor head velocity drops rapidly due to smaller diameter values (see FIG 9 the table values).

Thus, for the present invention, the bearings are for example / preferably designed as a hybrid spindle bearings (eg type XCB70 ..) sealed on both sides with appropriately adjusted lifetime lubricant and correspondingly far away from the fluid through the working space shaft seals, said working space waves -Abdichtungen next Abscheide- and defense facilities (see ima catalog from the WZ-Maschinenbau for spindle seals) still neutral collection / buffer rooms (13) as a protection as well as the unconditional (!) Prevention of any gas flow through the bearing, without exception need a safe bypass, so a gas-permeable bypass (channels, holes) with minimal flow resistance.

Instead of the aforementioned hybrid spindle bearings, of course, all-ceramic bearings are also feasible as well as if necessary. Magnetic bearings right up to the water store. ) The evaporator cooling for the work space components can be shown in FIG. 8 as a horizontal line with the pressure p ₀ ^* at t ₀ ^* represent, as exemplified in Figure 2: For differentiation, the ^* please note, because This pressure may well and specifically differ from the pressure p _o at t ₀ in the evaporator (35), if it is advantageous according to the application-specific process simulation. It is also possible to perform the evaporator cooling for the work space components via a separate refrigeration cycle. ) Instead of the rotor pairing with 2-toothed spindle rotor (2) and 3-toothed spindle rotor (3) as "Tribivari" other rotor pairings are conceivable (albeit probably less efficient), such as: rotor pairing as "SynchroVari" according to DE 10 2016 004 048.3 as well as the classic 2: 2-cycloid rotor pairing (but with blow hole) 6) The Control Unit (25) implements the respective application-specific requirements by the control unit (25) manages the entire system and intelligently regulates, controls and monitors. All relevant data are stored in the Control Unit (25) and are collected and evaluated. 7) The positive displacement machine according to the invention, hereinafter referred to simply as "Tribivari", is designed as an intelligent system, which is solved by the features and properties described below, where the abbreviation "ES" stands for the "electronic motor pair spindle rotor synchronization" according to the invention. This novel intelligence can be represented by the following special tools:

• (self) diagnostic tools

• Regulatory tools

The following somewhat more detailed explanations are intended to facilitate comprehensibility, even though there are inevitably some repetitions and "embellishments" to represent different perspectives with slightly different expressions (because of the other perspective, which certainly improves understanding).

A compressor works in principle between the following two limits:

• efficient compression (minimizing internal leakage, matching Iii value, effective heat dissipation, ... etc ...) as a soft boundary

• Avoidance of splitting (crash) as a hard limit

^> Challenge with these limits: (This applies especially to dry runners)

A) individually for each individual machine (manufacturing tolerances, assembly differences, etc.)

B) change during runtime (formation of deposits, contamination, wear, etc.)

C) depending on the respective operating point (esp. Pressure range, volume flow etc.)

D) vary with changing environmental conditions (hotter, colder, dirtier etc.)

Forex:

The more accurately each compressor is aware of its individual limits in its particular situation during its lifetime and usable (!), The better this system will be.

What can Tribivari do better than today's compressors ?:

Today's compressors (especially as dry runners) are designed to survive the worst-case scenario, ie: in the other operating points they are worse because of higher leakage.

Tribivari masters the heat consumption of all components for the respective compressor efficiency by "PartCool" at any time ^) and can therefore adapt to "all" conditions with running self-diagnosis and Δ-compensation! (Δ is generally for deviations and differences)

"PartCool" = CU intelligent guided cooling water flow per component,

plus approximation of internal compression ratio

The heat budgets of all components are finally individual (!) And always known & customizable under control, by using the algorithm in the CU to precisely set the respective cooling fluid flows. How does Tribivari make its individual ^{0 * 0} intelligence? :

° * ° individual = for every machine in every situation & environment at any time

► Check the relevant k ₀ speed ** and compare running with storage

► Measure flow resistance by ^ pressure difference degradation as a function of time

► Inverse cooling to determine the crash safety by ΔΤ as a temperature difference

► Measured value comparison with subsequent extrapolation

► ... etc. ...

The CU is used for the specific PartCool regulation thanks to an algorithm with targeted and comparative learning of deviations and differences.

Tribivari knows at any time how far its own load can be driven in each case to: a) safely avoid the crash (splitting waste)

and b) to intelligently maximize the compression efficiency for precisely this "situation" incl. c) to learn independently by comparison (!):

What was good? What was bad? => This leads to the respective optimum plus d) by extrapolation as prognosis with appropriate message to "top" (outside).

That is, Tribivari helps itself by repairing itself practically by hand.

What is the new Tribivari CU "intelligence"? [CU = Control Unit]

Unlike the currently only "aufgesattelten" (Screws could already work before) controls, the intelligence of Tribivari is a conceptual part of this new compressor technology by the entire operation under any conditions including their constant changes individually (ie specific to each Tribivari with Their very own tolerances and respective operating conditions / deviations) of the control unit with constant self-diagnosis (!) and prognosis with constant adjustment to the process under different conditions (colder / hotter environment, worse cooling etc.) is led. This is the novel Tribivari intelligence.

Today's compressors can not adequately adapt to the respective process and its changes, as well as to changing environmental conditions (eg hotter).

A) "oil-injected screws" = injected oil quantity (it is indispensable due to internal leakage, heat dissipation and lubrication) can not be adjusted arbitrarily with regard to oil quantity and oil temperature.

B) "dry-compressors" = they do not control all (!) The heat balance of their workspace components and therefore have only a good operating point (minimum gap) for crash avoidance (gap consumption) and otherwise work "unhappily" at extreme speeds ,

C) In addition, neither of these machines can adjust their internal compression ratio (ie, between over-compression and sub-compression) to the respective operating point (compare refrigerant compressor effort per housing slide).

Tribivari is fundamentally superior in that it fulfills 3 characteristics simultaneously:

Tribivari = dry PLUS eta PLUS μθ

Decisive is the PLUS of these features.

Because Tribivari controls the heat budget of all workspace components and namely: ♦ at any time = the CU permanently monitors the compressor and always regulates the cooling fluid flows via the so-called PartCool (as described)

♦ complete = both in terms of process and environmental conditions as well as all of them

Working space components

♦ flexible = different and changing conditions in the process and in the environment are met

♦ comprehensive = over cooling fluid mass flow and cooling fluid temperature suitable for any current situation and not only for one operating point, but always optimally for the entire work area

♦ synchronous = the workspace components are always synchronized (= always in step, no divergence)

♦ efficient = with always suitable heat dissipation (and not according to the motto: "Much helps a lot", but in each case fitting = intelligent!) The best polytropic exponent and no over- / under-compression for desired pressure & volume flow

♦ intelligent = with its own learning (!) Algorithm with self-diagnosis and prognosis even forward-looking

Specifically at Tribivari:

a) Control and control of the heat balance of all workspace components

b) so that thanks to actual gap differences over the size of the gap dimensions, the internal leakage (= entropy) can also be mastered

c) always adjust the internal compression ratio appropriately with additional partial outlet openings

d) optimize the height of heat dissipation polytropic exponent of compaction

e) and thus maximize the efficiency

f) the temperature level application-specific if necessary. adapt or control

g) by rotor speed and cooling fluid setting the gew. Conveying gas quantity and the nominal operating pressure.

What belongs among others to the "Tribivari_CU-intelligence" ?:

(better than Screw's just "saddled up" FU intelligence)

1) Play values Δ: = gap distances of the working space components:

Δ2.1 = 2z rotor to the housing

Δ3.1 = 3z rotor to the housing

Δ3.2 = rotors to each other

Δ as function f (z) possible. in rotor longitudinal axis direction

xy denotes integrally all gap distances

Purpose: · safe avoidance of gap-consumption (= crash),

• Knowledge of the size of the leakage column (for highest efficiency per operating point)

• That's not possible today

1 .1) Determination of the actual individual gap values (especially with regard to manufacturing tolerances and assembly differences) with each AirEnd assembly via peeling discs on the fixed bearing exactly adjusted per (!) Rotor according to: a) for Δ2 / 3.1 by contact + withdrawal

(... as an assembly-must ever rotor, unfortunately integral over £, not in operation ...)

b) for Δ2 / 3.1 by inverse cooling

(... also in operation after the co-rotational speed measurement, PartCool distribution)

c) for all Axy by co-measurement

(... clear, with PartCool adaptation, also in operation plus inverse cooling)

d) for Δ2 / 3.1 with hot rotors

(... inaccurate temp. level / fluctuations / duration)

e) for all Axy by espionage

(barely accessible)

f) for A3.2 via electronic synchronization

(... note: Δφ of emergency synchro-wheels is detected first)

1 .2) Determination of the changes of these gap values during operation according to A) to D) as current inference via measured value comparison u / o ko-speed u / o flow resistance as well as rotation angle-Δ with electronic synchronization ... = all with Interpolation and extrapolation

Self-diagnosis:

Evaluation by algorithm in the CU based on the individual gap values according to 1)

with determination of need for action incl. trend recognition (prognosis) with intelligent analysis plus vibration sensors (especially for bearing control)

Adaptation to the process, especially in the case of process changes:

(= much more than just today's speed adjustment)

Adapting to the respective process and its process changes by evaluating the differences in the algorithm and leading to consequences = e.g. Part Cool Customization

Adaptation to the environment, especially in the case of environmental changes:

Adaptation to different and changing environmental conditions

Efficiency Optimization:

always lowest energy consumption through optimal cooling regulation

not just for a single operating point (as before) but for the entire area

Temperature control:

Compliance with desired limit temperatures (esp. Sensitive process gases) Compression adjustment:

Change in internal compression ratio via additional partial outlet openings (15)

to avoid under- and over-compression

Purity of the pumped medium:

Adaptation of the size of the secondary gas flow to the neutral space per working area shaft seal BASIS:

Simulation algorithm stored in the CU, fed by the individual gap values and the current situation and correspondingly adapted reactions, based on maps that are constantly expanding and interpolated and compared (!) With constant learning.

Electronic synchronization:

each spindle rotor with own (synchronous) motor plus encoder,

Cooling fluid to the spindle rotor cooling thread passed through the hollow motor shaft (with simple coupling) Tribivari helps itself by practically repairing itself Tribivari by hand, ie:

Tribivari is so intelligent, by Tribivari with the mentioned (self-) diagnostic tools as so-called. "Self-diagnosis" initially recognizes itself when Tribivari changes due to wear, abrasion, contamination and / or deposit formation, and can then be adjusted from the above-mentioned Regulier tools its operating behavior, concretely this is e.g. at each operating point, as required by the user's process operating point in the particular situation,

a) set the most suitable gap values via PartCool or PartCool & Control,

b) each set the optimal internal compression ratio on Nach-inlet and / or pre-outlet, c) and set the most suitable rotor speed.

Based on the individual start state of this Tribivari system stored in the Control Unit, the current state (due to wear, abrasion and / or contamination, deposit formation possibly changed) of Tribivari is taken into account in the algorithm of the Control Unit as well as the current ones Ambient conditions (hot, colder, dirty heat exchangers, etc.) and the currently desired operating requirements (ie in terms of volume flow, pressure level, but also allowable power consumption in the sense of avoiding expensive power spraying, etc.).

Example 1 :

Tribivari uses its own (self-) diagnostic tools, ie, by means of co-rotational speed measurement and / or ΣΔρ measurement and / or algorithm-measured value comparison and / or Δφ-

Rotor pair check and / or inverse cooling ... etc incl. Any combination of these tools determines that the gap values have decreased in the outlet area, e.g. due to deposit formation / contamination. Tribivari can determine this via the algorithm in his own control unit, where individual guideline values (stored in the assembly of this tribivari) are available for the different measured values and are stored with the respective links, relationships and interpretations Measured values are compared. The control unit then adjusts the regulating tools as a regulation unit for this Tribivari system by, for example, PartCool reducing the cooling system for the compressor housing via the outlet-side cooling fluid flow (9.1 a) and / or the two cooling fluid flows (9.2 and 9.3 ) to the spindle rotors is intensified. If these diagnostic results (here as an example: gap values at the outlet are reduced) would not be known, there would be a risk that Tribivari would continue to cool the workspace components and thus increase the risk of splitting (= crash). Thanks to this approach according to the invention via the mentioned (self-) diagnostic tools and regulating tools, these limits are now known for each operating point and operating conditions, and Tribivari can not only be operated safely but also in the respectively optimum (in the least energy requirement) range. At least by inverse cooling, it can even be determined individually for each spindle rotor which gap value has decreased, namely Δ2.1 or Δ3.1, in order accordingly to determine the relevant cooling fluid flow 9.2 or 9.3 according to value tables {e. calculated by FEM simulations).

Example 2:

Tribivari determines via its own (self-) diagnostic tools that the gap values have increased in the inlet area, eg due to abrasion / wear, noticeable via worse compression behavior. To compensate for this situation (to "rescue"), for example, the cooling fluid flow to increase 9.1 b at the compressor housing inlet area. Based on "PartCool" as a self-diagnosis using:

Co-rotational speed measurement and / or χΔρ measurement combined with

Inverskühlung (at least as a safety check against crash)

Content and purpose:

Measurement of compressibility of a compressor at zero flow rate (ie only "counteracting" the internal leakage and not expelling fluid at the outlet) for different rotor speeds within Tribivari CU intelligence for the purpose of:

a) determination of the actual achieved individual compression quality level at the end of the assembly as a control and Okay approval (ie within the desired tolerance) stored in the own CU as a base-output reference for continuous comparison in the operation for the purpose of detecting a tendency and Forecast displayed by extrapolation.

b) On-the-fly self-diagnosis to detect changes (such as wear, abrasion, fouling, fouling, operational changes, such as in the process and / or in the environment, etc.)

c) Preferably, the co-rotational speed measurement is possibly combined with χΔρ measurement combined with the inverse cooling as an ongoing operational check for safe crash avoidance by means of extrapolation.

Procedure for co-rotational speed measurement:

If the inlet pressure is known at the closed outlet for different rotor speeds and thanks to PartCool at defined (!) Heat levels ^{** 00 of} the relevant (ie in particular the working space) compressor components (and the resulting individual gap conditions) the respective outlet (overflow) is reached -) Pressure measured and the quotient of exhaust to inlet pressure gives the sought Ko-speed value for this rotor speed, and thus as a value table or as a functional representation:

y-axis = ko value as quotient p _a / pi

x-axis = rotor speed nR

^** °° Because thanks to CU-intelligence means Part Cool & Control the heat budgets and thus, the gap values are selectively regulating and controllable via the thermal expansion of all the workspace elements, is individually defined Component temperatures each at the ko-speed measurement Compression quality level determined and compared to the base-output reference values and other measurements during operation, not only the current state but also the changes are recognizable:

ie self-diagnosis as well as prognosis and tendency.

In addition, the sufficient safety margin for crash avoidance is determined by means of the inverse cooling, that is to say for the stated working limits:

► both safe crash avoidance

and

► as well as efficient compaction

Inverse cooling = simulation of a "wrong" (inverse) component cooling with a component temperature difference, as it no longer occurs later in the operation (because constantly monitored by the CU in this sense)

Both co-rotational and inverse cooling are repeatedly used during operation to detect changes in the life of this compressor. Simplification:

The inverse cooling is also executable via CU-deposited algorithm as extrapolation of several "harmless" (in the sense of readily available) hot-fluid temperatures (preferably from the warm fluid reservoir (33), for example).

First as an overview: (then explained separately)

The following (self-) diagnostic tools belong to Tribivari intelligence (by way of example):

1) contact + withdrawal + fixation

2) inverse cooling

3) co-rotational speed measurement

4) ΣΔρ measurement

5) Algorithm Measurements Comparison

6) Δφ rotor pair check

7) combination & evaluation

8) ... etc. ... (... here are additional (self-) diagnostic tools can be supplemented)

And the following regulating tools belong to Tribivari intelligence (exemplary):

A) "PartCool", also called "PartCool & Control"

B) rij adaptation

C) FU speed variation

D) "ActionStep ReactionCheck"

E) combination & evaluation

In Tribivari spindle compressor according to the invention at least the temperatures mentioned in Fig. 1 are measured, not only from the cooling fluid but also from the components. This is very easy with the compressor housing and in the frame-fixed inlet and outlet area, because it is stationary (frame-mounted) components. In the case of the rotating spindle rotors, the relationships between cooling fluid temperatures and rotor temperature for the various load states are stored in the control unit (25) via previously performed simulation calculations and model calculations (eg by FEM), so that the "defined temperature - Ratios "for the entire Tribivari spindle compressor in the CU (25) are always known with sufficient accuracy or are to be converted via interpolations (known geometry and material properties) with the resulting individual gap conditions also widely known.

These "defined temperature ratios" are always a prerequisite for the correct use of these tools, which is ensured with sufficient accuracy thanks to the extensive temperature measuring points. (preferably similarly simple sensors as common in today's car construction and widely used)

In fact, since the temperature ratios are never exactly the same, the CU has an algorithm for converting to a uniform comparable state, which will henceforth be referred to as a defined temperature ratio.

Separate cooling fluid temperature ranges at the reservoir (10) facilitate the achievement of defined temperature conditions by cooling fluid is removed specifically for the relevant component. The following (self-) diagnostic tools belong to Tribivari intelligence (by way of example):

1) "Contact + Retraction + Fixation": (This only occurs when mounting the compressor stage)

During assembly, each finished ^{* 0 *} spindle rotor is inserted individually into the compressor housing (1) until complete contact with its housing bore as so-called. "Zero-gap" so touching, paying attention to as complete as possible support between the rotor and housing (if necessary. Check by means of Touchierpaste and slightly rotating by hand to secure the rotor-housing contact), which is why the housing is preferably vertical and the spindle rotor of is introduced above. Because the (average) inclination angle γ ₂ or γ ₃ between spindle rotor and housing bore is known, this rotor must now be pulled out again by a trigonometry directly calculable path Azweg in Rotorlängsachsrichtung and on the respectively adjustable distance / distance discs (34 and 35) between the inlet cover (16 or 17) and the compressor housing (1) are fixed to the desired (average) gap value Δ2.1 or Δ3.1 between the spindle rotor (2 or 3) and the compressor housing (1). to fulfill, wherein according to Fig. 6.a applies:

Δ2.1

on the 2z rotor: ^ ^Z path2

sin {y ₂ }

Δ3.1

and at the 3z-rotor: ^ ^Z Weg3 ^~~

sin {y ₃ ]

It must be ensured that the components (ie the respective spindle rotor and housing) have approximately the same component temperature, which is also to be logged or must be taken into account when entering the data in the CU memory (also to be entered into the CU ).

Advantageously, the gap size .DELTA.2.1 and .DELTA.3.1 can thus be set and logged in a targeted manner, which has hitherto not been possible. In this case, a constant inclination angle γ ₂ or γ _{3 is} advantageous, but are also stretch conform (ie according to simulation of the compression process and heat dissipation of the working space components) in Rotorlängsachsrichtung different angles of inclination possible, which is why then a mean inclination angle can be applied, or that inclination angle which mainly determines the gap dimension Δ2.1 and Δ3.1 according to the simulation of the compression process and the heat dissipation of the working space components.

^* ° ^* finished spindle rotors: as a rotation unit (40) with the respective inlet cover (16 or 17) completely assembled, in particular, the fixed bearing (10) is important for this process.

Inverse Cooling:

In the so-called "inverse cooling", the gap dimensions between the working space components are recorded and checked by the speed of the respective screw compressor being at minimum (or even zero = thus standstill) speed

♦ through the cooling fluid regions of each spindle rotor (2 or 3) preferably in sections via the transverse bores (29) in each case a liquid (for example water) with a continuously increasing fluid temperature

and or

♦ by the respective cooling fluid areas of the compressor housing (1) preferably in sections each a liquid is passed controlled with a continuously decreasing fluid temperature,

where constantly the still-rotation of the spindle rotors, for example, manually in the assembly or for self-diagnosis according to the invention in later operating pauses per Electronic motor pair spindle rotor synchronization is checked. Because of the different thermal expansions of these working space components, the respective rotatability of the spindle rotors will be terminated at a specific temperature level for this spindle compressor machine and based on the known material properties and the known geometry ratios are thus known for this screw compressor whose specific actual Kaltspielwerte individually stored in the CU (25) for this screw compressor.

Instead of the first touch as so-called. "Still-turning _limit " to go, but at least set a previously set for this spindle compressor machine _size ΔΤ _ΒΤ as a target component temperature difference _value and the simple (slow) rotatability control to ensure that there is no contact (touch) of the working space Components comes. In the later operation of this spindle compressor, the control unit (25) then knows how to set the respective cooling fluid flows of the working space components such that this AT _BT value is not exceeded, so that the crash can always be safely avoided. This targeted regulation of the individual screw compressor components is also referred to below as "tempering".

In addition to the simple still-rotation of the spindle rotors also be able to determine how the situation of the gap values actually and affects the compression behavior of the respective Tribivari plant, beyond the invention, the inverse cooling per AT _BT values verification is still linked with Measures performed as described under "Combination &Evaluation".

The AT _BT values are therefore to be regarded among other things as protection of the crash avoidance as still safe and several times by Inverskühlung examined component temperature differences of the CU in the enterprise always observed and kept, by the AT _BT values are not exceeded.

In particular, for higher compressor powers (for example, over 75 kW power), it is useful to use the inverse cooling partially selectively in the rotor longitudinal axis direction (as shown in Fig. 1) individual areas both spindle rotor-side and the housing side are specifically tempered with fluid, so that it is clearly recognizable how different the gap values in the rotor longitudinal axis direction are.

With these values, the "PartCool" can then be adjusted in such a way that the gap values in each area are optimal: optimal means that on the one hand crash (ie gap wastage) is safely avoided, which is thanks to the knowledge of the respective AT _BT values Now finally possible, and on the other hand, the inner gap leakage on the controlled by PartCool gap values according to the present simulation of the compression process is controllable so that the efficiency is maximized for exactly the currently present compression process.

For inverse cooling, the following case distinctions make sense:

Mounting inverse cooling:

Here, in the assembly, the actual start state is recorded specifically for each screw compressor after contact + retraction + fixation of its actual AT _BT values as mounting AT _BT values and stored in its control unit (25). In addition, linked measures are carried out as described under "Combination &Evaluation" and these individual measured values are stored in the CU for this Tribivari compressor. This process forms the reference reference for possible changes (due to wear, abrasion, contamination, deposit formation, etc.) during later operation. Use inverse cooling:

In the case of insert inverse cooling, the mounting AT _BT values are preferably repeated (or similar, in order to allow conclusions about the mounting AT _BT values by means of a stored algorithm in the CU ^{* 00 *} ) and combined with combination & evaluation the current status of this Tribivari system, so that this Tribivari system is operated optimally between working limits (in terms of efficiency as described).

The insert inverse cooling is preferably done during breaks in operation, in which case the higher temperature fluid for the fluid flow areas of each spindle rotor comes from a hot fluid reservoir (33). For this hot fluid reservoir (33), either during operation, a cooling fluid partial flow is diverted uncooled and there "warm parked" or selectively heated there by an electric heater generated there.

Of crucial importance here is the comparison of the currently determined values with the previous values, in order to be able to operate the Tribivari system optimally (ie avoiding a crash and at the same time best efficiency) and, on the other hand, to enable the trend and forecast.

^* °° ^* If this process of inferring is sufficiently secured with sufficient experience, extrapolation and interpretation can be omitted later on the use of warm fluid. Nevertheless, it sometimes helps to produce the defined temperature conditions. ko-speed measurement:

In the case of the co-rotational-speed measurement, the instantaneous compressibility of this spindle compressor machine is integrally checked, in particular the changes in the algorithm of the control unit being evaluated in the sense of adaptation of the PartCool and recognition of a tendency.

♦ Determination of the actual achieved individual compression quality level at the end of the assembly as a control and with an OK approval (ie within the desired tolerance values) in the own CU as base-output-reference filed for constant comparison during operation to detect a tendency and the prognosis by extrapolation.

♦ Self-diagnosis during operation to detect changes (for example due to wear, abrasion, contamination, deposit formation, operational changes, for example in the process and / or in the environment, etc.)

♦ Preferably, the co-rotational speed measurement is possibly combined with total pressure difference measurement combined with inverse cooling as an ongoing operational check for safe crash avoidance by means of extrapolation.

Procedure for co-rotational speed measurement:

If the inlet pressure is known at the closed outlet for different rotor speeds and thanks to PartCool at "defined temperature conditions" (Explanation = see above), the outlet pressure (overpressure) is measured and the quotient of outlet pressure to inlet pressure results in the sought ko Speed value for This rotor speed, and thus as a value table or as a function representation, eg according to:

y-axis = ko value as quotient p _a / pi

x-axis = rotor speed nR

^** °° Because thanks to CU intelligence, the heat budgets and the thermal expansion of all workspace components and the gap values can be specifically regulated and controlled by PartCool, the individually defined component temperatures in the co-rotational speed measurement Quality level and the comparison with the basic output reference values as well as further measurements during operation show not only the current state but also the changes: ie self-diagnosis as well as prognosis and trend (by means of extrapolation).

In addition, the sufficient safety margin for crash avoidance is determined by means of inverse cooling - for the stated working limits:

So both safe crash avoidance and most efficient compression. The co-rotational speed measurement as well as the inverse cooling are repeatedly used during operation to detect changes in the life of this compressor. ) integral pressure difference measurement, abbreviated as "χΔρ measurement":

During the χΔρ measurement, the current flow resistance of the respective Tribivari compressor stage is measured by setting a selected overpressure at "defined temperature ratios" with open inlet and closed outlet in the outlet collecting chamber (12) and with very slowly rotating (eg less than 10 revolutions per minute) spindle rotors the reduction of pressure in the outlet plenum (12) is measured for a selected period of time (eg 3 minutes). This individual χΔρ measurement takes place for the first time at the end of the assembly of each spindle compressor AirEnd and is referred to in the CU as so-called. "Basic reference" deposited. In the course of operations, this χΔρ measurement is repeated in the pauses at a selected rhythm controlled by the CU and compared both to the base reference and to all follow-up measurements. From this a prognosis and tendency can be deduced by extrapolation.

) Algorithm Measurements Comparison:

During operation, the CU (25) contains many measured values, regulatory actions and reactions as well as various evaluations. Based on the previously performed simulation calculations as well as (FEM) model calculations of the relevant compressor components, a steadily growing database is created, which is continued with the constantly incoming data. In the CU (25), these data are now constantly compared and interpolated using an algorithm so that they are also mapped ("modeled") and stored for applications that are not exactly as they are currently occurring (for example, higher production gas prices). Inlet temperatures), from which CU (25) the appropriate output signals (32. e) are given.

Initially, due to the even smaller amount of data, the comparison and interpolation will initially be coarse and unfocused with increased uncertainty; however, as the individual (very own) database grows steadily in the CU, these fuzziness gets smaller and the machine gets better and smarter.

) Δφ rotor pair check: with Δφ as the angle of rotation between the spindle rotors

When Δφ rotor pair check is individually for each Tribivari system, the gap situation Δ3.2 between the spindle rotors (2 and 3) via the electronic motor pair spindle rotor synchronization by measuring the exact rotational angular clearance for each shaft train via the rotary encoders (20 and 21) and with both the base reference from the assembly and the follow-up measurements is compared and evaluated in terms of the tendency and prognosis.

Action:

In the electronic motor pair spindle rotor synchronization then a motor string (ie each spindle rotor with carrier shaft fixedly connected to its drive motor rotor shaft) electrically blocked (thus detained) and the other motor string then checks the remaining rotation angle Δφ as so-called, remaining rotation angle play and stores this value. This measurement is repeated a number of times for the entire spindle rotor pairing, and the respective maximum and minimum values are stored and compared again (with basic reference and follow-up measured values), and at the correct values (ie within the stored tolerance ranges) the mean value Set as target specification for operation by electronic motor pair spindle rotor synchronization. With the electronic motor pair spindle rotor synchronization can over for the spindle rotor pair

► Reduced angular play values a formation of deposits or contamination

► Increased angular play values, abrasive wear or surface abrasion and wear

be determined with appropriate feedback by CU, for example, to higher-level maintenance and service stations.

7) Combination & Evaluation:

The (self-) diagnostic tools mentioned are not only to be used individually but also in combination and evaluated. For example, inverse cooling does not have to be driven until the first contact of the workspace components as a check of the still-rotatable limit (also because of the risk of surface damage) by the inverse cooling at an AT _BT value previously set in the CU ( Thus, a clearly defined temperature level of the working space components) on the one hand, the rotation is still guaranteed and on the other hand a χΔρ measurement and / or co-rotational speed measurement are performed, the then determined by these methods values are compared with that for this inverse cooling corresponding and stored in the CU base reference and comparison values.

A) "PartCool", also as "PartCool & Control":

The most important regulating tool is the individual control and regulation of the cooling fluid flows for each component over the respective quantity (mass flow) of the respective cooling fluid flow as well as over the respective cooling fluid temperatures. This is not a "stubborn" control, but a regulation or regulation in that the system response has a direct influence on the mentioned PartCool parameters, hence the term extension as "PartCool &Control". Virtually all changes in the Tribivari system as well as in the process as well as in the environment can be compensated by PartCool & Control, because thanks to the data stored in the CU for the respective work process (and "only" as an extra or interpolation of directly available data). as well as the expansion behavior and resulting gap values with corresponding inner gap leakage Values, etc., the respective corresponding compression behavior of the Tribivari system can be optimally adapted in each case.

B) rij adaptation:

In each work process different conditions prevail (for example with respect to pressure and temperature values, flow rate, ambient conditions, etc.), so that for the desired minimum Kompr.-energy needs adjustments in the compression process are desirable. These adjustments also the so-called inner compression ratio as an internal part n _r value of the compacting machine, the first purely geometrically describes the relationship from the inlet chamber to the outlet volume of chamber volume. About the actual compression ratios (esp. The respective temperatures and heat dissipation during compression) results in the known over- and under-compression, which is initially minimize as possible. The control unit of the Tribivari system according to the invention can now adjust the internal compression ratio of the current situation at any time ideal via the regulation of partial gas flows via additional Teilauslass openings (15): This regulating tool in operation is referred to as "n _r adaptation" ,

C) FU speed variation:

With this classic and well-known procedure, the spindle rotor speed is adapted to the respective conditions via FU < ^{= Fret} ^Inverter ", in particular with regard to the currently desired delivery medium volume flow: as is known, almost proportional to the rotor speed.

D) "ActionStep ReactionCheck":

Out by the control unit are continuously carried out small changes, such as the cooling fluid flow to a workspace component, such as the compressor housing and / or at selected intervals (eg a few minutes) in which n _r adjustment etc .. It is important that the ΔΤ _ΒΤ values stored in the CU are always observed for reliable crash avoidance (= important!). On the basis of the constantly incoming measured values (esp. Temperatures), it can now be determined in the algorithm of the CU whether this change has resulted in an improvement or deterioration in the current compression process, in particular via the energy recording detectable (ie engine torques and engine speeds , and / or only the motor current recordings).

Thus, "ActionStep ReactionCheck" is a constant self-learning and iterative method, which can be regarded both as a (self-) diagnostic tool and as a regulatory tool, because the system responses also draw conclusions about the current state of the Tribivari system discover.

E) combination & evaluation:

The aforementioned regulating tools are not only to be used individually, but in particular also combined and evaluated. Thus, for example, PartCool & Control and Iii adaptation via the CU's own algorithm are always carried out in a coordinated manner, preferably evaluated and performed in combination by ActionStep ReactionCheck. The filing of the results in the CU's own database constantly increases the knowledge of this Tribivari system and thus belongs to the Tribivari intelligence. For tribivari intelligence, the evaluation of measures carried out is an essential prerequisite for the above-mentioned regulations.

This evaluation is carried out according to the following characteristics:

with the abbreviation "ES" as "Electronic Motor Pair Spindle Rotor Synchronization" e.g. regarding "ActionStep-ReactionCheck":

Improvements are noted when, at an operating point at an existing pressure PB, the power requirement (which is even known per ES for ESR) is reduced or minimized at a known speed, with gap leakage and temperature feedback via the temperature feedbacks (32.e) Entropy balance in the algorithm of the CU thanks to simulations and ongoing learning (write down the "experience" of this machine) are assessed so that the Compr. Efficiency can be specified. This is henceforth referred to as an efficient compression process for the current situation.

A volume flow measurement for the pumped medium is generally too time-consuming, but would be a nice relief if it is carried out or is available.

Instead of improvements, of course, deteriorations in the compression behavior are also noticeable and are evaluated by the Control Unit, in order then to be able to initiate appropriate control measures (especially by PartCool & Control etc.).

Advantageously, the cooling fluid flows are application-specific for the particular situation according to the algorithm stored in the CU and flexibly based on current experience of the CU by the respective optimum is sought, in particular, the sufficient heat dissipation via a conventional external heat exchanger with advantageous temperature differences taken into account becomes.

This is inventively the new Tribivari intelligence, as it is simply not possible in the prior art.

The Tribivari system knows practically at any time with sufficient accuracy, how their individual status is currently (= how it is exactly, for example, with respect to pollution, deposit formation, state of wear, load capacity, temperature level, current gap values and compressibility, etc.) to To be able to optimally carry out the respective work process in the current situation (!), optimally in the sense of the most efficient compression in the current situation (!).

In addition, thanks to the trend and forecast analyzes mentioned, the CU will forward its status in good time to higher-level service and maintenance points in order to permanently ensure the maintenance, care, maintenance and service as well as the availability of this system.

The Tribivari system is designed to be self-learning by continuously updating the analysis data for each CU under the respective process conditions and continuously optimizing them further using ActionStep ReactionCheck and storing them in the CU's own database. Command values for CU intelligence: (!) = Important (-) = less important

1) (!) Cooling fluid flow to 2z rotor

(by speed of the own cooling fluid delivery pump or the regulating member)

2) (!) Cooling fluid flow to 3z rotor

(by speed of the own cooling fluid delivery pump or the regulating member)

3) (!) Cooling fluid flow to the housing = metered per section

(especially for larger machines, for example> 75 kW)

4) (-) Cooling fluid flow to the side parts (actually only to the outlet side part)

5) (-) Coolant flow to the lubricant (no longer with electronic synchronization)

6) (!) Rotor speed (via FU = frequency converter: possible without slip = synchro-motor)

7) (!) Additional partial outlet openings as variable partial gas streams

Measured variables:

a) almost all temperatures

esp. Prakt. all Temp.-differences ΔΤ to each cooling fluid flow and the conveying gas plus lubricant temperature

as well as the component temperatures (esp. on the housing and the side parts) b) rotor speed

c) Torque per rotor (with electronic synchronization)

d) any cooling fluid mass flow

(At least over the specifically regulated speed of the cooling fluid delivery pump / characteristic possibly possible) results with ΔΤ the heat dissipation per workspace component in each operating point at any time

Special features:

1) The actual gap values Δ2.1 and Δ3.1 and Δ3.2 are used when mounting the

Compressor individually per machine detects e.g. by "inversing" or

"Contact + Retraction" and stored in the CU, these values then operating the algorithm in the CU to regulate the different cooling fluid flows each

Align working space component such that on the one hand crash (ie gap consumption) safe (depending on the size of the machine, for example, with about 15%

Safety reserve) is avoided and on the other hand the gap values one

specified maximum value (depending on the machine size, for example, about 1.5 times the cold gap values from the assembly)

Because the CU is always familiar with the condition of the compressor due to the control of the heat balance and the thermal expansion behavior of the workspace components stored in the CU.

2) Self-diagnosis and prognosis

for determining, recording and evaluating the current state

esp. with electronic synchronization to the speed variation 3) Process Adjustment & Ambient Adjustment & Temperature Control & Compression Adjustment via Additional Partial Outlet Openings

4) Co-rotational speed measurement combined with inverse cooling for specific determination of the current (ie the current state) individual PartCool with PartCool & Control

Definition of "working space" = space between inlet (1 1) and outlet (12) The working space is determined by the pair of spindle rotors (2 and 3) and the surrounding compressor housing (1) with the narrow (in the range of 0.1 mm and smaller) gap values Axy of the respective components.

In the working space, the desired compression of the pumped medium takes place via the working space components, ie spindle rotor pair (2 and 3) and compressor housing (1).

In addition, according to the invention still applies that the CU as a control unit (25) monitors not only the screw compressor as described regulates and performs optimally, but the user with its complete system / factory control of the automation technology as industrial control in the so-called , "Process control technology" not only communicates (eg Profibus system) but also actively participates, for example, the load management for the entire (at least for this user) system, which consists of the individual compressor systems, each with its own CU (25), so is managed / regulated, so that, for example, expensive power peaks are avoided, which then belongs to the term "Industry-4.0". Here are (preferably) at the same time (if the user agrees) feedback to the (or which, if there are several) suppliers to the current state of the compressor system with all individual systems including forecast for further course with appropriate maintenance recommendation on the known Diagnostic systems (eg vibration sensors, temperature profiles, etc.) with the corresponding evaluations (software). It also includes the constant and constant adaptation to changing or changing process conditions, e.g. by covering, pollution, wear, etc., but also by external environmental conditions such as temperature level (eg warmer or colder environment) another desired pressure level, whereupon the intelligent CU system (25) responds by appropriate adjustment of the cooling water amounts, approximation of the inner Compression rate by means of additional Teilauslass openings (15), etc., as well as all measures for self-diagnosis to determine the current state of this compressor in this application and prognosis for the rest of the course with appropriate remedial action of adaptation of the cooling fluid quantities to the warning to the operator.

In the figures, a dot is simply set as the index instead of the subscript, so that e.g. R.F2 means RF2 and here denotes the root radius on the 2-toothed spindle rotor, where:

F stands for profile foot

K stands for profile head

C stands for cooling (cooling)

WK stands for pitch circle

2 stands for the 2-tooth spindle rotor (2)

3 stands for the 3-tooth spindle rotor (3) 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 displacement profile footing wall thicknesses w for the supporting foot base body (32) using the example of FIG -Rotors with detail to the steam outlet (14) over several (balanced with the necessary cross-section ^) transverse bores from the cylindrical evaporator cooling bore (6) with the radii values, which are carried out as follows: for the preferably blowhole-free profile pairing the gas delivery "external thread" (31) on the 2-toothed spindle rotor above the pitch circle line (37). Known, the drive motor (18) consists of a motor rotor (rotatably on the carrier shaft 4) and a motor stator package with the stator electrical windings (in vertical cross-hatching),

optional: Extraction to the vacuum pump (29) starts at the neutral chambers (13) of the working area shaft bushings, in order to protect the bearings from the pumped medium if necessary

Fig. 2 shows an example of a cooling circuit with diversion of t ₀ cooling fluid (9) from the circuit with cooling fluid injection (33) in the compressor working space per operating point targeted adjustment of the internal compressor volume ratio as iV value by additional partial outlet -Openings (15), with steam outlet (14) per workspace component, ie housing (1) and rotor pair (2 and 3), in the inlet space (1 1) shown

the expansion valve, which is still shown, is preferably replaced with water vapor as the circulation medium via the simple height difference with the use of gravity as the so-called hydrostatic pressure difference (the present illustration relating to the direction of gravity would then have to be adapted).

The control unit (25) receives and processes various signals to the current operating requirements, to the entire circulation system and esp. Also from the compressor according to the invention in particular via the Regulierorgane (38) to adjust the compressor components for each operating point such that the requirements are met in the best possible way - only with the Control Unit (25) can the system work reliably and efficiently (in practice a "New Intelligence").

Referring to PCT / EP2015 / 062376 = similar, but now improved by said inventive features to meet the water vapor requirements.

FIG. 3 shows, by way of example, a pair of spindle rotors with an adaptation of the [(z) - Nerte 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 would have to be represented three-dimensionally, for the different according to positions E, S, V and L according to FIG. 5

where for the (z) values:

^R _K2 ( ^z ) = μ ₂ ( ^ζ ) ³ ( ^ζ ) or: ^R _K3 ( ^z ) = μ ₃ ( ^ζ ) ³ ( ^ζ )

Adaptation of the [i (z) ANerte in the rotor pairing according to the invention, preferably as a 3: 2 pairing to fulfill the following 3 core tasks: • Maximizing the nominal pumping speed (with respect to the rotor pair cross-sectional area, it may be possible to reach a large surface area)

• with blowhole-free rotor mating (minimize internal leakage)

• with optimum use of the critical bending speed at each spindle rotor specific to its respective speed

Design: Each for the 2z rotor and the 3z rotor with different cooling hole 0 values Rc2 and Rc3

wherein the respective supporting steel shaft was not shown for simplicity, and

the head angle YF2> 90 ° so that the tooth cross-section at the 2-toothed spindle rotor (2) becomes somewhat slimmer without falling below a minimum head width bi <2 (e.g., 5 mm).

This happens in such a way that the bending-critical rotational speeds per rotor (ie for 2z and 3z) match, so that the following is achieved for the spindle rotor pair:

• The rotor pairing is without a blow hole, so that the internal leakage is reduced.

With reference to the illustrated rotor pair cross-section, this design achieves significantly more head area and thus an increased pumping speed relative to the cross-section, which is the aim of water vapor compression.

• In addition, the 2-toothed spindle rotor also has the larger cooling bore for heat dissipation during compaction, so that the component heat balance with regard to heat absorption and heat dissipation is improved.

The 2z rotor has a 1.5 times higher rotational speed than the 3z rotor and accordingly it is embodied according to the invention in such a way that this 2-toothed spindle rotor achieves the more rigid shaft thanks to RF2> RF3 at reduced (by means of YF2> 90 °) mass has, which has a favorable effect with respect. Increasing the critical bending speed, because the 2-toothed spindle rotor yes yes must also rotate faster and accordingly with the higher bending critical speed limit is carried out according to the invention.

• Accordingly, the slower 3z rotor has a lower bending critical speed due to the lower bending stiffness, but it also rotates slower.

According to the invention, the rotor pair is now designed in such a way that the critical bending speed at the 2z rotor is 1.5 times higher than the critical bending speed at the 3z rotor.

bending critical speed generally as the root of stiffness by mass

Fig. 4 shows an example as shown in FIG. 1 only on 3z rotor with external profile conveyor thread area below the pitch circle line (37), displacement profile area = where the outer conveyor thread (31) with tread teeth and tooth space areas, the respective working chambers form as a series connection between the inlet and outlet and below the pitch circle line (37) provide the blow hole-free compression. FIG. 5 shows by way of example: rotors of FIG. 1 and FIG. 3 paired

to illustrate the overall rotor geometry and pointing to the crossing angle alpha and the spindle rotor pairing with the center meshing engagement lens area

FIG. 6 shows by way of example a total of 4 CAD representations for:

6.a) compressor housing (1) designed as so-called. "Pot housing":

So outlet side closed bottom side and inside processing of the working space from the open inlet side

6.b) rotation unit:

each spindle rotor with carrier shaft, bearing, drive motor and measuring 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, dto. for the 3-toothed spindle rotor, where the cylindrical. Flattening (27) at the 2z rotor input is not yet shown.

6.c) Assembly and Game Setting:

for each of the two on peeling discs (26) for the important rotor head clearance to the housing, shown by way of example as a detail for the head clearance Δ2.1 between 2-toothed spindle rotor head and housing. The final clearance adjustment between the rotor heads and the housing takes place via peeling disks (26), this being illustrated by way of example as Δ2.1 in FIG. 6c for the 2-toothed spindle rotor head.

6.d) finished machine:

Both rotary 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 in turn is connected to the process control of the user is.

Compared to the pumped medium, the motor windings of the two drive motors (18 and 19) are protected, for example, by vacuum-proof potting the motor stator winding packages or by retracted gap between the motor stator and motor rotor, etc.

The rotor internal geometry according to FIGS. 1 to 4 with the cylindrical evaporator cooling bore has not flowed into FIG. 6, since this embodiment applies as described instead of the described evaporator component cooling via a cylindrical evaporator cooling bore (6) according to FIG. 2 This illustration now for the option with separate cooling water flow as cooling water operation according to the protection PCT / EP2016 / 077063, in this embodiment, a cylindrical internal rotor cooling is not required, because it suffices the internal rotor cooling shown in Figure 6.

In this Fig. 6 is shown:

♦ good and safe balancing for the rotary units esp. For the desired high speeds, the water vapor to about 350 m / sec as max. Rotor head speed can be performed.

♦ Simple assembly as a modular system, by different rotor pair variants in the same housing geometry

♦ targeted clearance setting via the peeling discs (26) in order to be able to compensate the respective tolerance situation (because all production parts have deviations / dimensional differences within certain tolerances) by unavoidable manufacturing tolerances "individually" (as exactly for these respective components).

♦ electron. Synchronization via (18) and (19) as drive for each rotation unit

♦ and with pC as the control unit for the intelligent cooling of the components (as described above) FIG. 7 shows by way of example: operating / operating points as a basis (Excel) state of the art = by turbo, improvement by means of the present invention by the higher ΔΤ in heat dissipation for t _c

more ΔΤ for the heat output below t _c desired

= a turbo today (already 2-stage working) can not do that

= there must be a displacer, which creates the p / p pressure ratio

= at the same time wg. Water vapor necessarily as absolute / complete dry runner

FIG. 8 shows, by way of example, an illustration of the compression process in the pressure-enthalpy diagram in the case of water vapor compression, showing the improvement due to the intensive evaporator heat removal during compression

• state of the art as a small line (with inscription)

Improvement according to the invention as dashed line (with inscription)

from [T] to [2] condensing

View Purpose:

Prior art by turbo, which must work in two stages with intercooling, compared to the improvement of the invention, here referred to as "HydroCom" (abbreviated HC) Explanation of the prior art:

In order to isentropically compress from 8 mbar (t ₀ = 4 ° C) to 48 mbar (t _c = 32 ° C) ^(Camot) , ^{intermediate cooling} is indispensable for two-stage turbo, as it would already be isentropically from 8 mbar to 48 mbar a temperature increase from 4 ° C to about 200 ° C without intercooling, inventive improvement:

Because of the enormous p / p pressure conditions at high isentropic exponent is to ensure the best possible heat dissipation during compression, which would otherwise lead to fatal (in terms of increased compressor power) high increase in compression temperatures, so that in accordance with FIG. 8 Practical almost at the dew line is compressed (ie better than isentrop), wherein the rotor pair cooling cost per to by the branched cooling fluid flow (9.2 and 9.3) in the refrigeration technology, the overall efficiency slightly worsened.

Thus, HC fulfills a stronger requirement profile according to FIG. 7 in that, according to the invention, improved HC works from 7 mbar = 2 ° C. to 96 mbar = 45 ° C., thanks to efficient heat dissipation during compaction.

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

Therefore, it should again be emphasized at this point that this is merely an example with which only one of many possible design options for the rotor pair design according to the invention is shown for demonstration purposes only. For some applications, it may be favorable that the cylindrical evaporator cooling bore (6) is designed in a multiple cylindrically stepped form, as a kind of "terraces" with the overflow edge as shown by way of example in FIG.

When cooling fluid is generally referred to here, it means the R718 known in refrigeration, which is naturally compressed at the chosen negative pressure as water vapor in the positive displacement machine according to the invention, or in liquid form as cooling fluid (9) for cooling the components by evaporation ,

Terms such as substantially, preferably, and the like, and possibly inaccurate, are to be understood as meaning that a deviation of plus or minus 5%, preferably plus or minus 2%, and more preferably plus or minus one percent, of normal value is possible. The Applicant reserves the right to combine any features and also sub-features from the claims and / or any features as well as sub-features from a set of descriptions in any manner with other features, sub-features or sub-features, even outside the features of independent claims.

In the different figures, equivalent parts are always provided with the same reference numerals with respect to their function, so that these are usually described only once.

Since the lowest temperatures for water vapor are above 0 ° C, for lower temperature values (for example for deep freezing), the combination with the refrigerant R744 as CO2 is advantageous (as a 2-stage solution, also known as "cascade").

The invention relates to the water vapor compression for the refrigeration, air conditioning and heat pump technology, both for right-handed and left-handed (Carnot) cycles. In order to improve efficiency and performance at the same time larger pressure range, a dry 2-shaft displacement machine is proposed as a spindle compressor according to the invention, the spindle rotors (2 and 3) have a rotor pair center distance, on the inlet side (1 1) at least 10% larger than on the exhaust side (12), driven by electronic motor pair (18 + 19) spindle rotor (2 + 3) synchronization and each spindle rotor is provided with an internal cooling, the crossing angle alpha between the two rotor axes of rotation in combination with the respective (z) value in Rotorlängsachsrichtung is carried out such that per spindle rotor a preferably cylindrical evaporator cooling bore (6) with minimal wall thickness w on supporting Fußgrundkörper (32) arises while taking into account the (preferably) blowhole-free profile design the gas delivery external thread (31) and "spindle rotor specific matching" bending critical Speed and conversion of the internal volume ratio as iV value, wherein the adaptation of the internal volume ratio in operation via additional Teilauslass-openings (15) and the gas delivery external thread (31) in the 2-toothed spindle rotor (2) preferably with cylindrical Flattening (27) is performed in the inlet area. I would like to mention

1 . Verdichterqehäuse with outer cooling areas and inlet side greater distance of the spindle rotor receiving holes as the outlet side, these bore axes are preferably intersecting (ie with zero pitch) or also crossed (or skewed) are designed with external cooling fins for a by means of control unit (25) guided cooling fluid flow rate (9.1), preferably with in rotor longitudinal axis sections of cooling fluid flow, for example according to (9.1a) and (9.1 b), wherein for larger rotor lengths (eg> 500 mm) more cooling fluid flow sections be performed on the compressor housing, and the compressor housing preferably as so-called. Pot housing of FIG. 6a is performed.

2. spindle rotor, preferably with 2-toothed gas supply external thread (31), short "2z rotor" called, preferably made of an aluminum alloy with good thermal conductivity (preferably above 150 W / m / K), rotationally fixed on supporting points (7 ) on a steel shaft (4) and inside a cylindrical evaporator cooling bore (6) with radius Rc2 having

3. spindle rotor, preferably with 3-toothed gas supply external thread (31), short "3z rotor" called, preferably made of an aluminum alloy with good thermal conductivity (preferably above 150 W / m / K), rotationally fixed on supporting points (7 ) on a steel shaft (5) and inside a cylindrical evaporator cooling bore (6) with radius Rc3 having

4. 2z rotor carrier shaft, with the 2z rotor rotatably connected to radius Rw2 (preferably pressed) with central cooling fluid supply hole (4.a), preferably in one piece at the same time also shaft for the 2z drive motor (18)

5. 3z rotor carrier shaft, with the 3z rotor rotatably connected to radius Rw3 (preferably pressed) with central cooling fluid supply hole (5.a), preferably in one piece at the same time also shaft for the 3z drive motor (19)

6. cylindrical evaporator cooling bore with radius Rc and length Lc for the respective spindle rotor, vzw. with cooling fluid guide grooves (16), cooling fluid distributor overflow grooves (17) and support points (7)

7. support points as a rotationally fixed contact between spindle rotor (2 or 3) and support shaft (4 or 5)

8. Synchronization teeth for the spindle rotor pair, with electronic synchronization as a fallback gear running for emergency, e.g. Power failure, whereby the motors then automatically switch to regenerative operation in order to be able to shut down controlled by their own power generation at higher speeds and only at the end (own power generation is no longer enough) prevents the gear spindle rotor contact.

As a fallback gearbox, no lubricating oil is required, and this toothing is performed with increased skip overlap (ie, larger tooth bevel angle) so that the profile overlap can be reduced by decreasing the tooth heights for smaller slip ratios in tooth engagement to reduce friction and hence wear. the tooth flanks vzw as protection. still received a dry-running coating.

9. Cooling fluid flow for cooling the compressor working chamber components, ie rotor pair and housing, either branched off from the circulation medium (34) according to the example in FIG. 2 or as a separate cooling fluid flow according to FIG. 6d in general, where for example:

9.1 Cooling fluid flow to the compressor housing, for larger rotor lengths (eg> 500 mm) can be divided into: 9.1 a Cooling fluid flow through a section of the compressor housing (eg housing outlet side) 9.1 b Cooling fluid flow through another section of the compressor housing (eg central area) Cooling fluid flow to the 2z rotor

Cooling fluid flow to the 3z rotor

Spindle rotor fixed bearing for receiving the gas pressure axial forces and

for exact fixing of each spindle rotor in the longitudinal axis direction

Conveying gas inlet collecting space for the conveying medium with the gas pressure po

(simplifying pressure losses in the lines are initially neglected)

Delivery gas outlet collecting space for the pumped medium with the gas pressure pc

(Simplifying pressure losses in the lines are initially neglected) neutral collecting / buffer space per working space shaft feedthrough with reduced compared to the system pressure gas pressure, preferably, for. generated by vacuum vacuum pump.

Steam outlet over several transverse bores after a shoulder with radius RD2 or RD3 per rotor

Additional Teilauslass-openings as branched conveying medium outlet partial gas stream with a regulating member (pressure difference valve) for adjusting the internal volume ratio

Cooling fluid guide grooves with the respective radius Rc per cylindrical evaporator cooling bore (6) with groove base surfaces at an angle of inclination ψ, which is preferably 170 ° ψ 180 °, and the cooling fluid guide grooves as a thread with the largest possible pitch = as in ( 31)

Cooling fluid distributor overflow grooves (with undersized cross-section) vzw. in the groove bottom of (16)

2z drive motor as a direct drive for the 2z rotor, vzw. designed as a synchronous motor

3z drive motor as a direct drive for the 3z rotor, vzw. designed as a synchronous motor

Rotary encoder for measuring the exact angular position of the motor 2z rotor carrier shaft (4)

Rotary encoder for measuring the exact angular position of the motor 3z rotor carrier shaft (5)

Frequency converter, referred to as "FU.2", for the 2z drive motor (18)

Frequency converter, referred to as "FU.3", for the 3z drive motor (19)

FU-Control-Unit, designated as "FU-CU", for both frequency inverters FU.2 (22) and FU.3 (23), where the FU-CU directly exchanges the operating data with the control unit (25).

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 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 iS of "Industry 4.0" Spacer / spacer discs, preferably as so-called. "Slicing discs" designed for individual fixing of the respective spindle rotor in the rotor longitudinal axis direction for targeted gap value adjustment as A2.1 value on the 2z rotor (2) or as A3.1 value on the 3z rotor (3) cylindrical flattening (as 2) over the radius RKE2 at its rotor inlet side circulation medium through the evaporator (35) for heat absorption (as a core task in refrigeration ) Vacuum pump to remove foreign gases and to generate the necessary negative pressure for the steam cycle, preferably in the neutral spaces (13) sucking to protect the (rotor) bearings. Water reservoir to compensate for water losses Gas delivery external thread with preferably blowhole-free profile rotor pairing to meet the compressor core task, namely to transport the gaseous fluid from the inlet (1 1) to the outlet (12) and thereby compressing Fußgrund -Body with wall thickness w at each spindle rotor (2 or 3) cooling fluid injection into the working space of the compressor Circulation medium through the condenser (36) for heat release (as a core task in heat pumps), circulation medium here water vapor (in the circuit by various Conditions running), but in principle also suitable for other circulatory media, both for right- and left-handed Carnot processes evaporator for the circulating medium, in which a quantity of heat is absorbed. Condenser for the circulating medium, in which a quantity of heat is released. Pitch circle line (abbreviation: WK) to the respective spindle rotor Regulierorgane for specific adaptation of the respective volume flow rate of cooling fluid flow (9), led by the control unit (25) Vibration sensors to detect altered residual imbalance suggestions by different amounts of cooling fluid per spindle rotor internal cooling unit rotation per spindle rotor system , each fully assembled and balanced, primarily consisting of:

• spindle rotor (2 or 3)

Carrier wave (4 or 5)

Synchronization toothing (8)

• Storage, with (10) as a fixed bearing plus working shaft seals, e.g. with 13)

Drive motor (18 or 19)

• Encoder measuring system (20 or 21)

a total of two pieces of rotary units (40) per spindle compressor vzw. is preferably PAGE INTENTIONALLY LEFT BLANK

Claims

claims

1 . Spindle compressor as working in the working space without operating fluid 2-shaft rotary displacement machine for conveying and compressing gaseous fluids, preferably water vapor, with a pair of spindle rotors in a compressor housing (1) having an inlet collecting space (1 1) and an outlet collecting space (12 ) having,

characterized in that the axial distance of the spindle rotor pair at the inlet end is at least 10% greater than at the outlet end, that each of the two spindle rotors (2, 3) by an electric motor (18, 19) is driven and an electronic synchronization Electric motors (18, 19) controls, and that the spindle rotors (2, 3) rotate without contact.

2. Spindle compressor according to claim 1,

characterized in that one spindle rotor (2) is bidentate, the other spindle rotor (3) is tridentate, and that the electronic synchronization is a 2 to 3 synchronization.

3. Spindle compressor according to claim 1 or 2,

characterized in that each spindle rotor (2 or 3) has an internal cooling, which preferably has a cylindrical evaporator cooling bore (6) with radius RC2 at the 2-tooth spindle rotor (2) or with radius RC3 at the 3-toothed spindle rotor (3). is executed.

4. spindle compressor according to claim 3,

characterized in that the evaporator cooling bore (6) has an internal structure with at least one of the following features, preferably several: a) at least one cooling fluid guide groove (16), preferably with more accurate (with deviation <1%) compliance with the Rc Value, especially with

a.1) groove base surfaces with inclination angles ψ (ζ) with 170 ° <ψ (ζ) <180 ° as f (z) and / or

a.2) the outlet area has a larger surface area for heat transfer than the inlet area,

b) cooling fluid distributor overflow grooves (17)

c) support points (7) for the rotationally fixed support on the respective carrier shaft (4 or 5) d) steam outlet (14) in the inlet space (1 1).

5. Spindle compressor according to one of the preceding claims,

characterized in that each spindle rotor system is designed with the final mounted and balanced rotary unit (40), and that preferably peeling discs (26) are provided for final clearance adjustment between rotor heads and housing.

6. Spindle compressor according to one of the preceding claims,

characterized in that at least one vibration sensor (39) is provided, which is connected to a control unit (25), and in that in the control unit (25), the supplied amount of the cooling fluid flow (9) to that for maximizing the total Efficiency corresponding amount is limited.

7. Spindle compressor according to one of claims 2 to 6,

characterized in that the bending-critical speed of the 2-toothed spindle rotor approximately (with a tolerance of preferably less than ± 30%), 1, 5-fold higher than the critical bending speed of the 3-toothed spindle rotor (3).

8. Spindle compressor according to one of the preceding claims,

characterized in that the crossing angle alpha between the two spindle rotor axes of rotation in combination with the respective

is carried out in the rotor longitudinal axis direction such that per rotor a cylindrical evaporator cooling bore (6) with minimal (ie with respect to the material strength matching the respective tooth height) wall thickness w on the supporting Fußgrundkörper (32) is formed (for example, according to the above position descriptions of E, S, V and L) while taking into account the (preferably) blowhole-free profile design of the gas delivery external thread (31) and "spindle rotor specific matching" critical speed and implementation of the internal volume ratio as iV value (as explained), wherein the gas conveyor External thread (31) on the 2-toothed spindle rotor (2) is preferably carried out with a cylindrical flattening (27) in the inlet region.

9. Spindle compressor according to one of the preceding claims,

characterized in that the regulation of the heat budget for the work space components is application specific as a base stage (as explained) in the component heat dissipation during operation to comply with the play values between avoiding the Spielaufzehrung and too large differences in the play values (as explained) and as the VET stage (as discussed) in component heat removal for efficiency improvement

• as branched cooling fluid flow

• as a separate cooling water flow

• via delayed evaporation

with cooling fluid injection (33) in the compressor working space, preferably in the region of the inlet collecting space (1 1), which is all regulated and controlled by the control unit (25).

10. Spindle compressor according to one of the preceding claims,

characterized in that each spindle rotor (2, 3) consists of an aluminum alloy and rotationally fixed on a steel shaft (4, 5) is pressed against the support points (7), and that preferably then only the gas delivery external thread (31) is manufactured and the spindle rotor (2, 3) has an already finished internal structure.

1 1. Spindle compressor according to one of the preceding claims,

characterized in that the adaptation of the internal volume ratio to the respective operating conditions via additional partial outlet openings (15).

12. Spindle compressor according to one of the preceding claims,

characterized in that a steam outlet (14) takes place directly to the inlet.

13. Spindle compressor according to one of the preceding claims,

characterized in that at the inlet of the 2-toothed spindle rotor, a cylindrical flattening (27) is provided, in particular that the gas delivery external thread (31) in the 2-toothed spindle rotor (2) has the cylindrical flattening (27) in the inlet region ,

14. Spindle compressor according to one of the preceding claims,

characterized in that the 2-tooth spindle rotor (2) is provided with an intermediate carrier (17), whereby preferably a weight reduction, in particular for a lower moment of inertia during startup (or deceleration) at the same time high flexural stiffness, for example, from vacuum-compatible fiber composite material , eg as CFRP material is reached.

15. Spindle compressor according to one of the preceding claims,

characterized in that at least one cooling fluid supply (9.2 or 9.3) is provided, that each spindle rotor has a cylindrical evaporator cooling bore (6) which is connected to the cooling fluid supply (9.2 or 9.3).

16. Spindle compressor according to one of the preceding claims,

characterized in that each drive has a hollow shaft, that the cooling fluid supply (9.2 or 9.3) to the cylindrical evaporator cooling bore (6) of the respective drive is effected by this hollow shaft, and that preferably the bearing (10) than for life designed bearings are, in particular life-fat-lubricated hybrid bearings, all-ceramic or magnetic bearings are.

PAGE INTENTIONALLY LEFT BLANK