JP2020505544A - Steam compressor including a dry displacement device acting as a spindle compressor - Google Patents

Abstract

The present invention relates to a spindle compressor designed as a two-shaft rotary positive displacement machine for transporting and compressing a flowing medium, in particular steam. The compressor comprises a pair of spindle rotors provided in a compressor housing comprising an inlet collection chamber (11) and an outlet collection chamber (12). The center distance of the pair of spindle rotors is at least 10% greater at the inlet end than at the outlet end. The two spindle rotors (2, 3) are driven by electric motors (18, 19), respectively, and the electric motors (18, 19) are controlled by electronic synchronization so that the spindle rotors (2, 3) are in a non-contact manner. Rotate in a state. [Selection diagram] FIG.

Description

Detailed description

  The circulation process is preferably characterized by a heat output and heat absorption and a compressor as a drive for the gas-phase circulation medium, based on Carnot's theorem. Circulatory processes are used quite frequently and are becoming essential in everyday life. This process includes clockwise and counterclockwise Carnot processes, in which the desired / targeted heat absorption results in a cooling operation (in the cooling and air conditioning field) or the desired / targeted heat output Thus, a heating operation (keyword “heat pump”) is performed using a heat exchanger that performs heat absorption and heat output. The transfer of the circulating medium generally requires a drive in the form of a compressor for the circulating medium in the gas phase. First, the circulating medium and its inherent properties are important. There are various artificial circulation media (generally produced chemically, such as HFC and HFO) and natural circulation media (ammonia, propane, propylene, isobutane, ethane, etc.).

  However, water is undoubtedly ideal as a circulating medium because of its generally high availability and: That is, water is completely non-toxic, can be used safely at low pressure in the form of steam, complies with the strictest guidelines and safety regulations, is resource-friendly, environmentally friendly, hassle-free maintenance, Efficient and practically without any risk (non-flammable, non-explosive, non-hazardous).

  The compressor has a problem because it requires an enormous flow rate in an operating pressure range of several mbar and also requires a very high pressure state. This results in a ridiculously difficult compression state, especially due to high temperatures, since the iso-entry compression index of the steam in this pressure range is very high, about 1.327. In contrast, recent refrigerants have a range slightly above 1.1, and the compressor temperature rises accordingly moderately.

  Vapor compression operations are nowadays performed using turbo compressors, but in order to cope with high pressure conditions, the compression must be performed in several stages simultaneously with the intercooling. The weakness in the basic characteristics of a turbomachine is that it produces only moderately satisfactory temperature and pressure conditions. Since steam has immense strength, a more efficient compressor scheme would significantly advance as a circulating medium.

  SUMMARY OF THE INVENTION The present invention is directed to (preferably) effecting the compression of steam by a positive displacement machine in a known operating region and pressure range, commonly referred to as low vacuum, wherein the positive pressure machine has the desired pressure differential and Large p / p pressure conditions are addressed by the typically steep characteristic curve of a positive displacement machine (i.e., pressure values above the volume flow at each corresponding operating point) and the machine is completely dry operated (No working fluid) and the overall efficiency of the whole system should be better in the whole application compared to current turbo compressors. This ensures that the demands of the user on cooling and heat pumps and other Carnot circulation processes are well fulfilled, especially for wide pressure ranges.

  Sub-atmospheric pressures (preferably from 6 mbar to less than 1 kW to well over 100 kW) as cooling cycle power in cooling technologies (ie industrial cooling, commercial cooling and building air conditioning) or as heat pump cycle power. Such purpose of compressing the vapor at 300 mbar, i.e. the standard low vacuum region) (the required compression force decreases according to the "COP" value (an example)) is the purpose of the gas inlet chamber (11) and the gas outlet. Achieved in the form of a two-shaft positive displacement machine based on the spindle compressor principle using a chamber (12), the center distance between the spindle rolls on the gas inlet (11) side is greater than the distance on the gas outlet (12) side and the intersection angle Since α is preferably 3 to 25 degrees, the following characteristics are obtained.

  The features according to the present invention are as follows.

1) Electronic synchronization. Since each spindle rotor (2 and 3) is driven by its own drive motor (18 and 19), each drive motor has its own FU (22 and 23) and each drive motor has a rotational angular position. Has its own measurement system (20 and 21) and a FU control unit (24), which controls the drive motors (18 and 19) via its own frequency converter (22 and 23). Are driven at corresponding speeds, so that the pair of spindle rotors (ie, 2 and 3) can operate without touching each other.

  The supply (9.2 and 9.3) of cooling fluid to the cylindrical evaporator cooling holes (6) of each rotor is additionally provided via the hollow shaft of the associated drive and the bearing (10) is It is preferably made as a grease-lubricated hybrid or all-ceramic bearing (or even as a magnetic bearing) for increased service life.

2) Cylindrical evaporator cooling holes (6) that function as "rotary cylinder evaporators" for self-cooling self-balancing. To evaporate the water, the spindle rotor coolant under pressure p ₀ ^* and temperature t ₀ ^* [these values include certain technical deviations, such as pressure drop, temperature rise due to unavoidable heat transfer] 2, by rotating centrifugal force at the cylindrical evaporator cooling holes, deviating from the circuit of FIG. 2, inevitably moves to the most urgently needed place at the present operating point during operation. The cylindrical evaporator cooling hole (preferably) has the following features based on the following description.

The design of the internal cooling of the spindle rotor according to the invention, the "rotary cylinder evaporator", is the most likely to solve the problem addressed by the invention, since the best possible heat transfer under centrifugal force is consistently achieved. Although it has favorable heat conduction properties, it is because the heavy liquid portion in the rotating cylindrical evaporator cooling hole causes the light gas component to move constantly from the heat conduction surface and evaporate again instantaneously, the following liquid part for conduction is performed a desired heat conduction reaches the rotor material and the additional simultaneously, by a cylindrical radius value is the same, in order to maximize the evaporation heat dissipation This is because the liquid part to be evaporated always moves by centrifugation where it is most needed and still reaches the longitudinal direction of the rotor, which results in a different power distribution at each operating point in the longitudinal direction of the rotor. As a result, the most efficient possible heat dissipation during compression can be achieved with a low cooling fluid supply (see values in FIG. 9) and a known high evaporation enthalpy difference, whereby according to FIG. The lines [1] to [2] are advantageously steeper and clearly better for the compressor than the isentropic profile.

  The following features apply to cylindrical evaporator cooling holes.

a) a spindle rotor positive displacement profile length L radius along _R to the length L _C containing R _C of the cylindrical evaporator cooling holes (6). The cylindrical evaporator cooling holes are preferably starting from between position E and the position S in the inlet region, preferably to reach the L past the outlet end, L the values of _R and L _C is the same (approximately Equal). The cylindrical evaporator cooling holes (6) are preferably provided as "internal structures" by means of cooling fluid guide grooves (16), cooling fluid distributor overflow grooves (17) and support points (7).

b) Cylindrical evaporator cooling holes (6) should be as cylindrical as possible (i.e., with a deviation far below 1%), for example, the manufacturing tolerance of the _RC value is It is desirable to set the _RC value to be larger toward the exit (that is, within the range of the position L).

c) The spindle rotor made of aluminum alloy can rotate in cooperation with the already created "internal structure", and in order to form this "internal structure", the cylindrical evaporator cooling hole (6) is preferably used. Is constituted by a cooling fluid guide groove (16) having a radius _RC and is provided with a plurality of support points (7), preferably by joining a warm aluminum rotor body to a cold steel shaft, for example, by a temperature difference of the components. Then, by fixed connection by temperature equalization, these support points press against the supporting steel shaft. Only then is the gas transfer "male thread" (31) formed, the wall thickness w being at a minimum and the heat of compression being dissipated, increasing the heat conduction through the short flow path.

  The groove bottom of the cooling fluid guide groove (16) is preferably designed such that a groove bottom with an inclination angle ψ (z) is formed, the inclination angle usually being called the z-axis, the inclination angle being at the z position in the direction of the rotor longitudinal axis. Accordingly, it is preferably in the range of 170 ° ≦ ψ (z) ≦ 180 °. Thereby, the distribution of the cooling fluid (9) along the rotor axis is such that the amount of cooling fluid is small (the amount of cooling fluid supplied is always limited and the total energy balance at a particular operating point is the highest efficiency) ), Depending on the current amount of cooling fluid suitable for the operating point, which is improved by a small filling section. Here, the cooling fluid guide groove is preferably a screw-like configuration having a pitch as large as possible. For example, in the case of a gas carrying male screw (31), the cooling fluid (9.2 and 9.3) is supplied to each rotor. In order to minimize the amplification of residual imbalance by doing so (since all liquids collect in the rotating system at the largest possible distance from the current point of rotation, thereby amplifying the residual imbalance). For example, when the pitch of the cooling fluid guide grooves is zero, the filling amount is very small.

  The effect of this residual imbalance amplification is to utilize, according to the present invention, to simultaneously minimize the amount of cooling fluid (9.2 and 9.3) supplied per rotor, and to use vibration sensors (eg, (Used for bearing monitoring) shows residual imbalance amplification with an excessive amount of cooling fluid in the corresponding rotor system, with different rotor speeds (rotation speed of 2t rotor is always 1.5 times) Therefore, since it is possible to accurately determine in which rotor the amount of the cooling fluid is excessive, the control device (25) performs the correct adjustment in the present example (the minimum required amount of the cooling fluid by the adjusting member (38)). (In the sense).

d) In order to compensate for the deviation and to distribute as much as possible the water evaporated in the longitudinal direction of the rotor in the cylindrical evaporator cooling holes (6), the bottom of the cooling fluid guide groove (16) of radius _RC Additionally, a small cooling fluid distributor overflow groove (17) is provided, which is arranged at a greater distance from the rotor axis than the _RC value, but at the same time The water contained therein has a small cross-section that wets the bottom of the cooling-fluid guide groove (16) of radius _RC beyond the cross-sectional area of these cooling-fluid distributor overflow grooves (17).

Of course, in the present description, the embodiment of the cylindrical evaporator cooling hole (6) is merely an example, the supporting point (7) and the cooling fluid guide groove (16) of radius _RC , and the cooling fluid distributor overflow groove. (17) is provided. Of course, other embodiments are also conceivable.

e) The addition of cooling fluid (9), especially to the rotor, is always critical, in the sense that it limits sporadic and even pulses and maximizes overall efficiency. Avoid equilibrium and minimize the amount of diverted cooling fluid stream (9). This is because there is actually no circulating medium (28) in the evaporator (35) during heat absorption. Thus, the cylindrical evaporator cooling holes (6) in each spindle rotor contain only the large amount of water currently required for evaporation at a particular operating point (eg, with a + 1% tolerance, which is conventional in the art). I do.

f) The minimization of this cooling fluid flow (9) is known and simple, e.g. for measuring the degree of filling in a particular cylindrical evaporator cooling hole (6) for each spindle rotor (2 and 3). This can be achieved by measuring with a vibrating center (eg, for rolling bearing monitors), but this will result in residual imbalance in the rotating system as the amount of water in a particular cylindrical evaporator cooling hole (6) increases. Due to the amplified and different speeds of the spindle rotor (the two-tooth spindle rotor rotates 1.5 times faster than the three-tooth spindle rotor), the unbalanced excitation is applied to the rotation system of the two- or three-tooth spindle rotor. Because they can be related, the cooling fluid volume (9.2 and 9.3) is adjusted based on the minimum volume. Thus, water is supplied in an amount currently required for evaporation at the current operating point.
Of course, other approaches can be used to minimize the cooling fluid flow (9).

3) The steam outlets (14) in the cylindrical evaporator cooling holes (6) of each spindle rotor are such that each cylindrical evaporator cooling hole (6) is formed by radius _RC2 or _RC3 , and the steam outlet (14) is Preferably, behind a step on the radius R _D2 or R _D3 , realized by transverse holes arranged in equilibrium with respect to each other, wherein R _D2 and R _D3 in a particular spindle rotor have corresponding cylindrical evaporator cooling holes It is characterized by being slightly smaller (i.e. a few millimeters, e.g. 2-5 mm) than the corresponding R _C2 and R _{C3 of} (6).

4) Cooling fluid injection (33). This selectively affects the carrier gas temperature in the working space, the space between the inlet collection chamber (11) and the outlet collection chamber (12).

5) With regard to the heat dissipation of the working space components, ie the spindle rotor and compressor housing (1) pair described in (2) and (3) above, this heat dissipation is very important for dry running machines. A distinction is made between two stages.

A) Basic stages of component heat dissipation:
The heat dissipation of the components of the working space is always ensured by a reduction in the play between the components of the working space (usually leading to compressor failure or “collision”) at all operating points, Can be used as a basis for protection and assurance.

  This requirement is, for example, by reducing the heat dissipation of the compressor housing (1), ie by reducing the corresponding cooling fluid flow (9.1) with a minimum cooling fluid flow (9.1). Since play has already been achieved with a small amount of cooling fluid (9), play is not threatened by the thermal expansion of the components of the working space.

  At the same time, in the case of this basic stage of heat dissipation of the components, it is necessary to ensure that the play value (ie the distance value between the components of the working space) is within a certain range, ie the minimum play value during operation is Since it is about 0.03-0.09 mm (depending on the overall dimensions, for large machines with a center distance of more than 150 mm, the value is more than 0.05 mm), the basic stage for heat dissipation of the operating components is In addition to ensuring that the above-mentioned reduction in play is suppressed (the absolute minimum requirement is that the minimum play value receives a safety margin of about 20% to 50%), the play values of other operating points are also reduced. Due to the different thermal expansion behaviors of the components, compared to a lower play value, it is twice as large as up to three times larger, since this is ensured by the basic stages of the heat dissipation of the components during operation This allows the control device (2 ) Through the, for the first time can be achieved in dry operation machine (previously could not be realized only by a wet rotor).

B) FCT phase with component heat dissipation:
(FCT (Final Compression Temperature) represents the final compression temperature, ie, the temperature of the medium conveyed at the end of compression, usually the highest gas temperature, and the FCT is usually measured in the outlet chamber (12).) The power required during compression (and exactly what happens in this compressor provided in the form of a "positive displacement machine") is reduced overall, thus minimizing the temperature rise in that volume during the compression process. If it can be suppressed, the efficiency (effectiveness) of compression can be improved. It is known that the heat dissipation required during compression also depends on the temperature difference between the gas in this volume and the heat dissipation surface around the components of the working space, but also the heat transfer coefficient (steam Is known to be a very high value) and heat conduction (the reason why it is preferable to use an aluminum alloy as the material of the spindle rotor). Thus, if the surfaces of the components of the working space can be kept cooler by the cooling flow, the heat dissipation during compression will be better and the temperature rise of the transported gas in the transported and compressed working chamber volume will be higher. Because of less, the compressor operating line becomes increasingly steeper, such as the line between points [1] and [2] illustrated in FIG.

  This typically reduces the demand for compression power and consequently improves (and is higher) efficiency.

6) Corresponding parameter design (ie crossing angle, rotor length, inlet and outlet center distance, head and root radius values per end face section, step slope, depending on the application specific requirements of the compressor design according to the invention) And the number of stages, and the cooling fluid flow (9) for heat dissipation of the components of the working space depending on the "internal structure" and the design of the spindle rotor versus the cross section, can be described by the following two approaches.

Divided cooling fluid partial stream (exemplified in FIG. 2 as cooling fluid stream (9)): As illustrated in FIG. 2, the cooling fluid stream (9) is diverted from the actual circuit as a partial stream and is being compressed. It is considered a preferred solution because it allows maximum heat dissipation through the cylindrical evaporator cooling holes (6). The only disadvantage is that this diverted cooling flow fluid (9) is separated from the mainstream and is lost when heat absorption takes place in the core task in the field of cooling technology, namely the evaporator (35). In a heat pump, a partial flow of the diverted cooling fluid is not lost from the circulating medium (34) if the heat output in the condenser (36) represents a core task.

Therefore, the following principles apply:
In a method specific to the present application, the advantage gained by reducing the compression temperature in the above-described FCT stage during heat dissipation of the components results from the reduced amount of cooling fluid (28) passing through the evaporator (35). If greater than the disadvantage, the diverted cooling fluid stream (9) should be realized by a cylindrical evaporator cooling hole (6), as illustrated in FIG. The quantity of 9) should be adapted to the specific requirements profile in a targeted and controlled manner, in the sense that in each situation it is regulated by the controller (25), only such quantity is By being diverted as a cooling fluid stream (9), the increased compressor efficiency due to heat dissipation results in an overall improvement over the aforementioned disadvantages with the associated auxiliary effort due to the diverted cooling fluid stream (9). Energy considerations More advantages are brought about. If such an approach is no longer feasible for some applications, the "alternative cooling water flow" described below applies.

Another cooling water flow: (illustrated in FIG. 6d) The advantage gained by reducing the compression temperature in the aforementioned FCT stage during the heat dissipation of the application-specific component is that the cooling fluid through the evaporator (35) If less than the disadvantage caused by the reduction of the quantity (28), another cooling water flow as shown in FIG. 6 with internal rotor cooling as described in PCT / EP2016 / 077063 should be realized. Yes, this ensures that the play between the components of the working space is reduced unconditionally, independently of the circulating medium.

  The advantage that the compression temperature is somewhat accidentally reduced by this additional cooling water flow which reduces play is certainly included. Of course, the available cooling water temperature is important and it is generally not possible to provide a valid guideline and therefore must be determined separately for each particular application. Thus (simply stated), the available cooling water temperature is different in hot environments (countries near the equator) and in cold regions (Siberia in winter) at any given time.

・ Evaporation delay:
According to the invention, if the evaporation of the cooling fluid (9.2 or 9.3) does not occur in the cooling fluid guide groove (16) due to a large acceleration value, the following is further provided. That is, the cooling liquid (which is also heated by absorption of the heat of compression) is withdrawn by the pitot tube (for example, as described in DE 102 01 300 9040.7 or DE 10 2015 10 8790.1) and by a high kinetic energy, because having a pressure higher than P _C, at some point after the compression step, for example, returned to the circuit at the outlet collection chamber (12), where the said liquid to absorb again heat in accordance with the operation by evaporating Therefore, the amount of the cooling fluid can be adjusted to increase the overall efficiency.

  In any case, for a particular operating / working point of the controller (25), the correct cooling fluid volume is adjusted (with respect to efficiency and imbalance minimization) and the corresponding data is obtained (for example according to a suitable process simulation). It is stored in the control device. "Trial and error" is also used as a self-learning process, in which the system itself attempts to change and, using the reactions (ie, energy demand and net output), is itself, with maximum efficiency, relative to the current operating point. Determine the settings that will be achieved. This approach is also called the "action" approach.

  Therefore, which of these approaches best solves application-specific tasks must be individually determined.

7) According to the invention, the auxiliary partial outlet opening (15) allows the internal volume ratio to be adapted to the current operating point, the partial outlet opening preferably opening in a spring-loaded manner, As the partial gas flow approaches the outlet in this working chamber, the pressure is higher than the pressure in the outlet collecting chamber (12) by allowing the partial gas flow to escape from the particular working chamber to the outlet collecting chamber (12). As a result, harmful over-compression in the working chamber (which adversely affects efficiency) is prevented.

  The internal volume ratio (ie, the quotient of the working chamber volume between the inlet and the outlet), as the “iv value”, is the best possible method for the current operating point that provides the most efficient (ie, energy saving) compression. To prevent harmful over or under compression. In operation, the iV value can be adapted according to the invention by using an auxiliary partial outlet opening (15), but first needs to be determined by a spindle rotor pair design. The iV value is basically affected by the following three variables.

The center distance between the rotation axes of rotation (variable due to the intersection angle α between the rotation axes of rotation, the distance at the gas inlet (11) being greater than the gas outlet (12));

Using the following formula at each point z in the rotor longitudinal direction, the ratio of the rotor head radius to the center distance at the end as a μ (z) value. Further, the root angle γ _F2 is intentionally selected such that the notarized pump capacity is maximized. The exact method is described in detail below.

The longitudinal gradient of the rotor (also determines the number of stages, ie the number of closed working chambers between inlet and outlet). It is known that the length of the rotor is as long as possible up to the critical bending speed. When determining the rotor-to-parameters described above, the "internal volume ratio" is defined as the "iv value" (i.e., the quotient of the volume of the [large] inlet and [small] outlet working chambers), and the iso-entry compression index of the transport medium, especially It should be configured according to the compression process for heat dissipation (ie, compression) during changes in working chamber volume, and the desired compression ratio (ie, quotient of outlet pressure and inlet pressure).

  For example, this relationship is shown with reference to the values described in FIG.

The following compression ratio is obtained by compressing the carrier gas (steam) to, for example, 7.0 mbar to 95.9 mbar.
95.5 ÷ 7.0 = 13.7

  Only in the case of isothermal compression (ie there is no temperature change during compression) an internal volume ratio of 13.7 is realized here as well.

  According to the present invention, an increase in temperature in the working chamber during "polytrope" compression results in an iV value of about 10 starting from the current isosteric compression index for the above in the range of about 1.327, with an iV value of about 10 Since it is obtained by intensive heat dissipation during compression by the evaporator cooling holes (6), both over and under compression are prevented.

  The iV value is, according to the present invention, as the change in working chamber volume obtained by the product of the cross-sectional area of the associated spindle rotor pair and the longitudinal extension of the rotor (generally ascertained by the profile gradient): It is technically realized by the formula.

a) By changing the cross-sectional area of each of the end face cross-sections (schematically illustrated as a plan cross-sectional view in FIG. 3) in the longitudinal direction of the rotor, the cross-section of the inlet-side rotor pair is larger than the cross-section of the outlet-side rotor pair. growing. The cross-sectional change in such a pair of spindle rotors is achieved as follows:
Changing the center distance according to the intersection angle α between the two rotor shafts,
Change the height of the profile tooth at the above-mentioned μ (z) value at each z position.

Such a change in the cross-sectional area in the rotor pair due to a change in the center distance and the μ (z) value gives an “iv.aμ value” (see FIG. 9), in which the working chamber expansion is taken into account. There is a need. In this example, each spindle rotor has a cylindrical evaporator cooling hole (6) having an _RC value, while taking into account different critical bending speeds at the same time as shown in FIG. The main body (32) must be provided parallel to the minimum wall thickness w.

b) Change in profile gradient (commonly referred to as m) in the longitudinal direction of the rotor:

Changing the profile gradient gives an "iV.m value" (see FIG. 9 as an example), which is usually significantly greater (more than 3 times) than the "iV.aμ value". Rotor length L _R over number (i.e., the total number of the working chamber between the inlet and the outlet) is the number still acceptable in view of the critical bend for "mesh limit" (tooth gap width It is also necessary to take into account the observation of how deep the tooth gap can be made.

  Naturally, these two changes simultaneously act synergistically in the longitudinal direction of the rotor to reach the desired overall iV value, in this example = 10, as illustrated in FIG.

  It is known that the higher the total iV value, the greater the heat dissipation during compression and the lower the compression temperature generally leads to improved compressor efficiency (ie, increased effectiveness).

  Here, if the operating point deviates from these mentioned pressure values, an efficient compression process is always ensured, since the auxiliary partial outlet opening (15) is ideally adapted to the current operating point.

8) Each spindle rotor (i.e., an aluminum part mounted on a steel shaft) consists of three regions.

a) Gas carrying male screw (31)
The gas-carrying external thread (31) is preferably formed with a joint rotation and connection to a steel shaft in order to minimize the magnitude of the wall thickness w of the root body.

b) The wall thickness w (32) of the root body minimizes resistance to heat dissipation and maximizes heat dissipation accordingly.

c) The "internal structure" consists of a cylindrical evaporator cooling hole (6) with a support point (7), at the outlet side (for example a lateral support sealed by a О ring, and a cylindrical evaporator cooling hole (6). ) Comprises an inlet-side steam outlet (14) for cooling fluid evaporated from a cooling fluid flow (9) for each working space component.

9) As an example, the spindle rotor design according to the present invention will be described with reference to four positions in the longitudinal direction of the rotor (the number of positions may be more or less than the above, and the spindle rotor design according to the present invention is independent of the number. 1 and 4 and FIG. 5, the following applies to the following positions from the gas inlet (11) to the gas outlet (12)).

  In this case, the following rules apply to each position (generally referred to as z) in the longitudinal direction of the rotor. The "μ (z) value" per spindle rotor in the profile design of each z position of the gas carrying male screw (31) of each spindle rotor is as follows.

R _K2 (z) = μ ₂ (z) · a (z) or R _K3 (z) = μ ₃ (z) · a (z)

Also, when μ ₂ > 0.6, the root angle γ _F2 is intentionally selected by making it larger than 90 degrees, and the head cylinder width b _k2 (z) falls below a selected limit value, for example, 5 mm. Never.

a) Position E:
According to the invention, at a radius R _KE2 , the maximum between the rotation axes of the spindle rotors on the inlet side at the end of the pair of rotors, with a cylindrical flat part (27) on the inlet side of the two-toothed spindle rotor (2). The distance a _E value spreads the maximum / maximum rotor head speed over a wider spindle rotor area, and preferably allows a uniform transition with a radial transition illustrated as “R. tan” in FIG. become.

b) Position S: (It can also be shown as a range extending over a plurality of z values)
Using the largest μ value, preferably, the inlet working chamber is adapted to meet the above boundary conditions (ie, cylindrical evaporator cooling holes, wall thickness at the support base body (32), blow hole degrees of freedom, critical bending speed, etc.). In order to receive the maximum possible volume without loss, the μ values according to FIG. 3 and the equations given for each z position in the longitudinal direction of the rotor are intended to be realized, as illustrated in FIG. You.

c) Position V: (can also be shown as a range spanning multiple z values)
By adapting the wall thickness to the reduction of the cross-sectional area according to the height of the teeth, a good heat transfer property is obtained while providing internal compression in the support root body (32).
Position L: (can also be shown as spanning multiple z-values) Preferably, as illustrated in FIG. 1, a cylindrical shape suitably designed to project beyond the end of the external thread and into the outlet chamber It is the end. Preferred specific values for these locations are illustrated in FIG. 9 as a look-up table. The emphasis in this table is merely exemplary, as both other locations and other values are feasible. The parameters referred to in FIG. 9 merely represent significant embodiments that illustrate the "spirit" of the present invention. In this example, each position can be reliably realized not only as a single z position, but also as a range extending over a plurality of z values in the longitudinal direction of the rotor.

10) According to FIG. 5, the intersection angle α between the two spindle rotor rotation axes is given in combination with a specific μ (z) value in the longitudinal direction of the rotor, so that each rotor is supported at the base body (32). A cylindrical evaporator cooling hole (6) with a minimum wall thickness w (eg, according to the above description of the positions of E, S, V and L) above (ie with respect to the material strength matching the tooth height) While having, based on the (preferably) blowhole free rotor profile design of the gas-carrying external thread (31) and the conditions of critical bending speed and internal volume ratio according to the above-described embodiment, "appropriate for a particular spindle rotor" Critical bending speed "(*).

  * "Suitable for a particular spindle rotor" means that a two-toothed spindle rotor that rotates 1.5 times faster according to the speed difference between the two spindle rotors has both higher bending stiffness and relatively lower rotational mass. This means that the critical bending speed is realized equally by both spindle rotors.

11) The critical bending speed ω _critical of the two spindle rotors is determined by the parameter design of the rotor itself (ie, from the viewpoint of diameter = stiffness)

However,

Is generally the square root of stiffness to mass (including bearings).

  In order to obtain high speeds, each rotor system according to the invention is embodied as a rotating unit (40), as illustrated in FIG. 6b, which brings a balance to the complete rotating unit (40). This is very important because the equilibrium quality is improved.

  The reason for this is that it forms a rotating unit that cannot be further individually balanced as one unit, which is later assembled (this is virtually always the case in prior art two-axis positive displacement machines). Even individual components that are well balanced generally have a balanced quality that is better than a rotating unit that is individually balanced and unchanged thereafter, as illustrated in FIG. 6b. Bad things are well known.

12) During assembly, each spindle rotor is individually inserted into the compressor housing (1) until the spindle rotor head first contacts the housing hole, then each rotor is pulled out and the separation plate (26) is removed. By fixing each rotor through the gap, a play adjustment between the spindle rotor and the compressor housing by means of the separating plate (26) is performed, thereby making the worn rotor head as illustrated as Δ2.1 in FIG. 6c. And a housing.

13) For bearings, the following rules must be observed:
Since bearings are a single element in contact and wear is inevitable, special care must be taken to design them. Therefore, the following rules must be followed for bearings.

In the case of steam, the bearing force is very weak (in both the axial and radial directions) and the main load is caused by high speed, which is known in bearing technology to use the nd _m coefficient as a speed characteristic. The product of the average bearing diameter (mm) multiplied by the speed (rpm = 1 / min), in which case the machine tool structure under the keyword "spindle bearing" would give clear design recommendations To provide. If this speed characteristic exceeds 1 million mm / min, special emphasis must be placed on speed resistance and lubricity. The rotor speed is due to the maximum permissible rotor head speed below the supersonic speed of the transport medium in the operating region. According to FIG. 9, a value with a sufficient safety margin has been selected in a table containing 350 m / s as an example, since the limit value for steam in the pressure range is specified at approximately 400 m / s. According to the invention, the two-tooth spindle rotor (2) is cylindrically flattened even in the inlet region, and therefore has a small diameter value, so that the speed of the rotor head decreases rapidly in the outlet direction. In this region, the speed limit is not suddenly reached (see the values in the table of FIG. 9).

  According to the invention, the bearing is configured as a hybrid spindle bearing (for example of the XCB70 type), for example / preferably sealed on both sides by a properly fitted permanent lubricant, and properly separated from the transport medium by a working space shaft seal, The working space shaft seal comprises, besides the separation and protection means (see the ima catalog of the machine tool construction of the spindle seal), an intermediate collecting / buffering chamber (13) which provides protection and emergency rejection of any gas flow through the bearing. A safe bypass, that is, a gas permeable bypass (flow path, hole, etc.) with the least flow resistance is always required.

  Naturally, a complete ceramic bearing can be applied instead of the hybrid spindle bearing. In addition, a magnetic bearing and further a water bearing can be applied as needed.

14) The evaporator cooling of the components of the working space can be represented as a horizontal line with p ₀ ^* at t ₀ ^* according to FIG. 8, as illustrated in FIG. The symbol ^* is used for distinction, which, if advantageous according to the application-specific process simulation, makes it possible to make the pressure limited and distinctly different from the pressure p ₀ at t ₀ in the evaporator (35). This is because it can be done. It is also possible to provide evaporator cooling of the components of the working space by another cooling cycle.

15) Instead of a paired rotor with two teethed spindle rotor (2) and three teethed spindle rotor (3) as "Tribivari", a rotor pair such as "SyncroVari" according to DE 102016004048.3. Other rotor pairs are also conceivable (but probably less efficient), such as standard 2: 2 cycloid rotor pairs (but with blowholes).

16) The controller (25) fulfills the requirements for the specific application, and the controller (25) manages the entire system, intelligently adjusts, controls and monitors. All relevant data is stored and collected in the controller (25) and evaluated.

17) The positive displacement machine according to the present invention (hereinafter simply referred to as "Tribivari") is designed as an intelligent system, which is described by the following features and characteristics, where the abbreviation "ES" stands for "Book". 1 represents “Electronic motor-spindle rotor synchronization” according to the invention. Such new intelligence can be demonstrated by the following specific tools:
・ (Self) diagnostic tool ・ Adjustment tool

  The following more detailed description is intended to facilitate an understanding of the present invention, but based on considerations from different perspectives, the use of slightly different terms (which will certainly enhance understanding because of the different perspectives) Vigorous, repetitive expressions and "decorations" can occur.

  The compressor operates in principle with the following two restrictions.

・ Efficient compression as soft limit (minimization of internal leakage, appropriate π _i value, effective heat dissipation, etc.)

・ Avoids gap reduction (collision) as a hard limit.

☆ Issues related to the above limitations (especially applied to dry runners):
A) Differences between individual machines (manufacturing tolerances, assembly differences, etc.)
B) Changes during runtime (sediment formation, dirt, wear, etc.)
C) Dependence on specific operating point (especially pressure range, volume flow, etc.)
D) Changes due to changing ambient conditions (hotter, cooler, more dirty, etc.).

☆ Summary:
The better the individual limitations in each compressor's particular situation are understood and useful (!) During its use, the better the system.

  Tribari advantages over current compressors:

  Current compressors, especially as dry running machines, are designed to withstand the worst-case scenarios. That is, at other operating points, the quality is low in that there is much leakage.

  Tribari has an ongoing self-diagnosis and Δ-compensation with “PartCool” by always managing the thermal status of all components (!) Regarding the effectiveness of the compressor! (Δ generally represents deviations and differences) allows adaptation to the “all” state.

“PartCool” = sum of cooling water flow + internal compression ratio matching intelligently guided by each component CU.

  The thermal state of all components is ultimately confirmed individually (!) At any time and can be adjusted by using the CU's algorithm to selectively set the associated cooling fluid flow. It is.

☆ How Trivivari provides individual ^* intelligence:
^* "Individual" means every machine in any situation and environment at any one time.

> Verify k ₀ Speed ^**, performs measurement> inverse cooling as a function of the flow resistance time due to decreased continuously compare> sigma pressure difference between recorded values, as the temperature difference, the safety collision against ΔT Confirmation> Compare measured values with subsequent extrapolated values. . . Other.

  The CU is used to adjust a particular PartCool by an algorithm with target deviation and difference compensation, learned by comparison.

☆ Tribivari always checks how much its own load can be driven each time,
a) Do this until the collision is safely avoided (gap reduction), and
b) intelligently maximize compression efficiency for exactly that situation,
c) do their own comparisons (!), including knowing individually:
That is, what was good? What went wrong? → This leads to related optimizations,
d) Further, extrapolation is performed as a prediction that the corresponding notification is “upward” (outward).
In other words, Trivivari actually adjusts itself and assists itself.

What is the "intelligence" of the new Tribivari CU? [CU = controller]
Unlike the currently only “sub-assembly” (pre-functioning screw) controls, Trivivari's intelligence is a conceptual part of the new compressor technology, which means that the overall operation is independent Individually by the controller under all conditions, including diagnostics (!) And expected constant changes with the current adaptation to the process based on various conditions (cooler / hotter environment, poor cooling) (I.e., especially for each Tribivari with its own tolerances and specific usage conditions / deviations). This is the new Tribivali intelligence.

  Current compressors are not well adapted to current processes and changes thereto, as well as changing environmental conditions (eg, higher temperatures).

A) "Oil filling screw" = the amount of oil injected (essential for internal leakage, heat dissipation and lubrication) cannot be arbitrarily adjusted with respect to the amount of oil, the temperature of the oil.

B) "Dry compressor" = Since the compressor does not manage all (!) Temperature conditions of the working space components, only one good operating point (minimum clearance) for collision avoidance (clearance reduction) Otherwise, it operates "improperly" at maximum speed.

C) In addition, all of these machines can adapt their internal compression ratio (ie the ratio of overcompression to undercompression) to the current operating point (see the operation of the refrigerant compressor for the housing slide). Can not.

Trivivari is fundamentally superior in that it satisfies three characteristics simultaneously. That is,
Tribivari = dry + η + μC
The important thing is that these features are added.

  This is because Tribivali manages the temperature conditions of all working space components as follows.

Always = The CU permanently monitors the compressor and constantly adjusts the flow of the cooling fluid with the so-called PartCool (described above)

◆ Complete = related to both process and environmental conditions, as well as all appropriate working space components,

◆ Flexibility = Allows various changing conditions during the process and in the surrounding environment,
◆ Comprehensive = Suitable for the current situation, depending on the mass flow rate of the cooling fluid and the temperature of the cooling fluid, not only for one operating point, but always optimal for the entire operating area,
◆ Synchronization = The components of the working space are always managed synchronously (that is, always stepwise and managed without deviation),
◆ Efficiency = always appropriate heat dissipation (and not just the motto of “better”, but in each case = intelligent!), Best polytropic index and no over / under compression of the desired pressure and volume flow,
◆ Intelligent = A self-learning (!) Algorithm that can be said to be positive based on self-diagnosis and prediction.

* Specifically, Tribivari allows you to:
a) monitoring and management of the temperature conditions of the components of the entire working space,
b) As a result of the above, due to the actual gap difference, internal leakage (= entropy) can be dealt with using the gap size,
c) Always adjust the internal compression ratio appropriately using the auxiliary partial outlet opening,
d) optimizing the degree of heat dissipation relative to the polytropic index of compression,
e) maximize effectiveness,
f) If necessary, adapt or monitor the temperature level in an application-specific manner.
g) Adjust the rotor speed and cooling fluid to provide the desired carrier gas volume and set operating pressure.

  In particular, those that form part of "Tribivari_CU-Intelligence" are as follows.

(In the case of screws, it is currently better than the only "semi-assembled" FU intelligence)

1) Play value Δ = gap distance between components of working space Δ2.1 = between housing and 2-t rotor Δ3.1 = between housing and 3-t rotor Δ3.2 = between rotors Δ It is shown as a function f (z) that can be realized in the longitudinal direction of the rotor.
Δxy represents the integral for all gap distances.

Purpose:
・ Avoid gap reduction (= collision)

・ Knowledge on the size of the leak gap (for maximum efficiency per operating point)
・． . . Currently impossible .

1.1) The actual individual air gap value of each airend assembly (particularly with respect to manufacturing tolerances and assembly differences) is detected through a fixed bearing separator correctly set for each (!) Rotor according to:
a) Regarding Δ2 / 3.1, due to contact + detachment (... assembly is required for each rotor, not for operation but for the entire l ...)
b) For Δ2 / 3.1, due to back cooling (even during operation after measuring the k ₀ velocity of the PartCool part)
c) For all [Delta] xy, by _{k 0} determined by applying the (... PartCool, ensuring even during operation in + reverse cooling)
d) For Δ2 / 3.1, due to the hot rotor (... incorrect temperature level / fluctuation / duration)
e) For all Δxy, by monitoring (... barely accessible)
f) For Δ3.2, by electronic synchronization (... note: Δφ of emergency synchronization wheel is detected first)

1.2) Detect changes in the gap value during operation according to A) to D) as continuous conclusions regarding the comparison of measured values and / or k ₀ speed and / or flow resistance and rotation angle Δ with electronic synchronization. . . . = By interpolation and extrapolation in all.

2) Self-diagnosis:
The evaluation by the CU algorithm based on the individual air gap values described in 1) determines the necessity of operation including intelligent analysis + trend detection (prediction) using a vibration sensor (especially for bearing monitoring).

3) Adaptation to the process, especially for process changes: (= far more than the current speed adjustment)
Evaluate differences in algorithms and adapt to specific processes and their process changes by leading to action measures = eg PartCool adjustments.

4) Adaptation to the environment, especially when the environment changes:
Adapts to various changes in environmental conditions.

5) Optimization of effectiveness:
Optimal cooling adjustments over the entire area, rather than just one operating point (as in the prior art), always minimize energy consumption.

6) Temperature control:
Adjust to the desired limit temperature (especially sensitive process gas).

7) Compression adjustment:
Changes in the internal compression ratio through the auxiliary partial outlet opening (15) avoid under- and over-compression.

8) Purity of transport medium:
Adjust the size of the secondary gas flow to the intermediate chamber per working area shaft seal.

9) Basic:
The simulation algorithm stored in the CU, provided by the individual void values and the current situation and the correspondingly adapted response, is based on a map that is constantly extended, interpolated and compared with a constant learning It is.

10) Electronic synchronization:
Cooling fluid is supplied via a hollow motor shaft (with one clutch) to the cooling screw of each spindle rotor with its own (synchronous) motor and encoder.

Trivivari automatically makes the auto-correction essentially alone:
That is, Trivivari has its own (self) diagnostic tool in the form of “self-diagnosis”, which itself first recognizes changes in Trivivari due to wear, abrasion, dirt and / or deposit formation, and then Automatic control is possible when the control tool can adjust the operation behavior based on the operation behavior, specifically, for example, at each operation point, at the user's process operation point in a specific situation. Means the following. That is,

a) Set the most appropriate air gap value by PartCool or PartCool & Control,
b) each optimal internal compression ratio is set behind the inlet and / or through the front of the outlet;
c) The optimal rotation speed is set.

  The current ambient conditions (higher and lower temperatures, heat exchanger fouling, etc.) and the currently desired operating requirements (ie volume flow, pressure level, as well as acceptable in the sense of avoiding costly power peaks) As well as the current state of the Tribari system (e.g. wear, wear and / or fouling, deposit formation, etc.) based on the individual starting state of the Tribari system recorded in the controller. ) Is taken into account in the algorithm of the control device.

Example 1
Tribivali is a proprietary (self-) diagnostic tool: k ₀ speed measurement and / or ΣΔp measurement and / or algorithm measurement comparison and / or Δφ rotor pair inspection and / or back cooling, and any of these tools ( Using the evaluation) combination, it is determined that the gap value has decreased in the exit region due to, for example, formation / dirt of deposits. In Trivivari, such a determination can be made by an algorithm of a control device of Trivivari, and individual guideline values (stored at the time of assembling the present Trivivari) can be used for different measurement values, and each contact point can be used. , Relationships and interpretations are recorded and compared to subsequently obtained measurements. Thus, the controller may, for example, say that PartCool reduces the cooling of the compressor housing by means of the outlet cooling fluid flow (9.1a) and / or reduces the two cooling fluid flows (9.2 and 9.3) to the spindle rotor. With regard to strengthening, the adjustment of the adjustment tool is performed as an adjustment device of the present Tribivari system. If these diagnostics are not known (here, by way of example, a drop in the air gap value at the outlet), the Tribivali may continue to cool the components of the working space, resulting in a reduced air gap ( = Collision) increases the danger. Thanks to the approach according to the invention with the (self) diagnostic and adjustment tools, the above limits for each operating point and operating conditions can be immediately known, so that the Trivivari can not only operate safely but also have an optimal (minimum energy) It can operate in the range of the meaning of the request. It is even possible to determine individually at least which clearance value has been reduced for each spindle rotor due to back-cooling, ie 2.1 or 3.1, and accordingly the associated cooling fluid flow 9.2. Or 9.3 increases according to a numerical table (for example, a value calculated in advance by FEM simulation) existing in the CU.

Example 2
Trivivari determines with its (self) diagnostic tool that the gap value has increased in the inlet area due to wear / wear, for example due to insufficient compression behavior. To compensate for this condition ("rescue"), it is necessary, for example, to increase the cooling fluid flow 9.1b in the inlet region of the compressor housing.

The following is based on “PartCool” as a self-diagnosis.
That is, the k ₀ velocity measurement and / or the ΣΔp measurement are combined with back cooling (at least as a safety check against a crash situation).

Content and Purpose For the following purposes, measure the compressor compressibility at zero flow for different rotor speeds and within the range of TribivariCU Intelligence (i.e., only suppressing internal leakage, the discharge of the transport medium at the outlet is Not performed). That is,

a) The individual compression quality levels actually obtained at the end of assembly are stored in a control group and Okay approval (ie, within the desired tolerance) stored in the CU of the system itself as the base output criteria for successive comparisons made during operation. ), A tendency is detected, and a prediction indicated by extrapolation is performed.

b) Perform a self-diagnosis during operation to detect changes (e.g., caused by wear, wear, fouling, deposit formation, operational changes in the process and / or environment, etc.).

c) In order to perform reliable collision avoidance by using extrapolation, it is desirable that a combination of k ₀ speed measurement with back cooling and ΣΔp measurement can be performed as a continuous operation test.

Procedure for k ₀ Speed Measurements If the inlet pressure is known, the resulting outlet (excess) pressure is the compressor component at the closed outlet for various rotor speeds and also related by the PartCool (ie especially in the working space). The measured quotient of the outlet-to-inlet pressure, at the specified temperature condition ^**** (and the resulting individual gap condition), gives the desired k ₀ speed value for that rotor speed, thereby giving a numerical table Obtained as a function expression.
y-axis = _{k 0} value x-axis is the quotient _P a / _{P i} = rotor rotational speed _{n R}

^**** The CU intelligence with PartCool & Control, in addition to the temperature condition, the thermal expansion of all the working space components, it is possible to adjust and control in a manner that the gap value and the target, in the case of _{k 0} velocity measurement, Individually defined component temperatures are used to determine specific compression quality levels and, in addition to comparing basic power reference values, make additional measurements during operation, so that not only current conditions, but also changes It becomes clear. Self-diagnosis and predictions and trends.

In addition, a safety margin sufficient to avoid a collision is determined by back cooling. That is, it is determined for the following operation limits. That is,
> Safe collision avoidance and> The most efficient compression possible.

  Back cooling refers to "inappropriate" (reverse) components that take advantage of this temperature difference because the component temperature difference does not occur anymore during operation (in this sense, it is also constantly monitored by the CU). It is a simulation of reverse cooling.

Both the k ₀ speed measurement and the back-cooling are used repeatedly during operation to detect changes in the useful life of the compressor.

Simplification:
Backcooling is also an algorithm stored in the CU as an extrapolation of some "harmless" (in the sense of being readily available) hot fluid temperature (preferably, for example, from the warm fluid reservoir (33)). It can be executed by

First, as an overview (separate description):
The following (self) diagnostic tools belong to Trivivari Intelligence (as an example).
1) Contact + drawer + fixed 2) opposite the cooling 3) _{k 0} velocimetry 4) Shigumaderutapi Measurement 5) Comparison 6 algorithms measurements) test 7 of Δφ rotor pair) combinations and Evaluation 8) Others (... more (specific ) Diagnostic tools can also be added here).

In addition, the following adjustment tools belong to Tribari intelligence (one example). That is,
A) "PartCool" (also called PartCool & Control)
B) π _i conformity
C) FU speed change
D) "ActionStep-ReactionCheck"
E) Combination and evaluation.

  In the Tribivari spindle compressor according to the invention, at least the temperature described in FIG. 1 is measured not only for the cooling fluid but also for each component. Measurements are very easy in the compressor housing, and in the inlet and outlet areas fixed to the frame, since they are stationary (frame-mounted) components. In the case of a rotating spindle rotor, the relationship between the cooling fluid temperature and the rotor temperature for various load conditions is stored in the controller (25), so that the "predetermined temperature condition" described below for the entire Trivivari spindle compressor is always Utilizing the well-known individual gap conditions, which are sufficiently accurately recognized in the CU (25) or likewise known, can be transformed by interpolation (known geometry and material properties).

  This "specified temperature condition" is a continuous prerequisite for the correct use of the above tools and is guaranteed with sufficient accuracy due to the wide range of temperature measurement points (preferably today's automotive manufacturing Simple sensors similar to those used in industry and widely used).

  Since it is impossible for the temperature conditions to be exactly the same, an algorithm is installed in the CU to convert to a similar comparable state. Hereinafter, this will be referred to as the term “specified temperature condition”.

  Different cooling fluid temperature ranges in the reservoir (10) facilitate the achievement of defined temperature conditions by selectively removing cooling fluid with respect to associated components.

The following (self) diagnostic tools belong to the Tribivari Intelligence (example):
1) "Contact + Draw + Fix": (Only occurs when the compressor stage is assembled)
During assembly, each completed ^*** spindle rotor is individually inserted into the compressor housing (1) until it is completely in contact with the hole (so-called “zero gap”), ie until contact is obtained. . Here, it is necessary to make the contact between the rotor and the casing as complete as possible (confirmed by the adhesive paste and slightly rotated by hand to ensure the contact between the rotor and the casing). Preferably upright, the spindle rotor is inserted from above. Since the (average) inclination angle gamma ₂ or gamma ₃ is known between the spindle rotor and the housing hole, pulled out the rotor, over a path distance Delta] z _path that is directly calculated by trigonometry, again in the rotor longitudinal axis, The spindle rotor (2 or 3) and compressor housing (1) are fixed between the inlet cover (16 or 17) and the compressor housing (1) via an adjustable distance / spacer plate (34 or 35). It is necessary to satisfy the desired (average) gap Δ2.1 or Δ3.1 between the body (1). According to FIG. 6a, the following applies.

For 2t rotor:

For 3t rotor:

The component temperatures of the components (i.e., the spindle rotor and the housing) must be approximately the same, which is also the case when entering data into the CU memory (even when entering the CU). Must be recorded or considered.
Advantageously, the gap sizes Δ2.1 and Δ3.1 can thus be set and recorded in a targeted manner, which is not possible with the prior art. In this example, it is advantageous to have a constant inclination angle γ ₂ or γ ₃ , but according to the law of expansion in the longitudinal direction of the rotor (ie by simulating the compression process and dissipating the heat of the working space components) different inclination angles are obtained. It is also possible to apply the mean inclination angle, or depending on the simulation of the compression process and the heat dissipation of the components of the working space, mainly the gap sizes Δ2.1 and Δ3.1 It is also possible to apply a defined tilt angle.
^*** Completed spindle rotor : in the form of a rotating unit (40) whose corresponding inlet cover (16 or 17) is fully assembled, in which fixed bearings (10) are particularly important in the process.

2) Back cooling:
In "back-cooling", the size of the gap between the working space components is measured and confirmed at the minimum speed of the spindle compressor (or even at zero = stationary).
The liquid (e.g. water), whose fluid temperature is constantly rising, passes in a controlled manner through the cooling fluid area of each spindle rotor (2 or 3), preferably in some areas, through transverse holes (29). And / or 液体 the liquid, whose fluid temperature is constantly decreasing , is guided in a controlled manner, preferably in some area, through the various cooling fluid areas of the compressor housing (1),
Here, for example, with regard to the self-diagnosis according to the invention, either manually at the time of assembly or during a later stoppage due to the synchronization of the electronic motor with the spindle rotor, the postrotation of the spindle rotor is constantly checked. Due to the different thermal expansions of each working space component, the rotatable nature of the spindle rotor ends at a certain temperature level with respect to the spindle compressor, and the specific actual cold play value of the spindle compressor depends on the known material. It can be known based on characteristics and known geometric conditions and is stored in the spindle compressor CU (25).

However, instead of using the first contact as a "post-rotational limit", at least one predefined ΔT _BT should be established as a set point element temperature difference value for the size of the spindle compressor. Yes, a simple (slow) rotational monitor should ensure that the contacts of the working space components are eliminated. During post-running of this spindle compressor, the controller (25) always knows how to adjust the specific cooling fluid flow of the working space components so as not to exceed the _ΔBT value, Collisions can be reliably avoided. The targeted adjustment of the individual screw compressor components is also referred to below as “temperature control”.

In addition to the simple post-rotation of the spindle rotor, in order to be able to determine the actual situation of the clearance value and thus how it affects the compression behavior of the Tribivari system, according to the invention, Further back-cooling is performed by examining the ΔT _BT values which are also relevant to the measures in the description under “Combination and evaluation”.

In this way, the ΔT _BT value is still considered to be reliable, especially with regard to collision avoidance protection, and the temperature difference of the components, which is confirmed many times by back cooling, does not exceed the ΔT _BT value during operation. As such, it is continuously observed and maintained by the CU.

  In particular, when the output of the compressor is high (for example, at an output exceeding 75 kW), the temperature of each region on both the spindle rotor side and the housing side is selectively controlled using a fluid (as shown in FIG. 1). 2) Since it is effective to use the back cooling partially and selectively in the longitudinal direction of the rotor, it is possible to clearly recognize how much the gap value in the longitudinal direction of the rotor differs.

Using these values, "PartCool" can be adjusted in a manner adjusted during subsequent operations to optimize the gap value in each region. "Optimal" means that, on the one hand, the safe avoidance of collisions (i.e. reduction of the gap) is ultimately feasible, since on the other hand the respective .DELTA.T _BT values are known, on the other hand, the compression According to the current simulation of the process, the clearance values managed by PartCool can be used to monitor internal clearance leaks, meaning that efficiency can be accurately maximized for the actual compression process.

In order to perform reverse cooling, it is appropriate to make the following distinctions. That is,
a) Assembly related back cooling:
In this case, during assembly, after contact + drawer + fixing, against especially the spindle compressor, the recorded actual original starting situation [Delta] T _BT value as a mounting [Delta] T _BT value, stored in the controller (25) Is done. Also, as described in the "Combination and evaluation" section, the relevant measurement is performed and the individual measurement values are stored in the CU of the Trivivari compressor. The process constitutes a criterion for possible changes during subsequent operation (due to wear, wear, fouling, deposit formation, etc.).

b) Use-related back-cooling For use-related back-cooling, preferably the assembly ΔT _BT value (or a similar value that allows the assembly ΔT _BT value to be determined based on an algorithm stored in CU ^{* °° *} ). Link with iteration, combination and evaluation to identify the current state of the Tribivali system.

  The use-related back-cooling is preferably performed at the interruption of operation, when hot fluid flows from the warm fluid reservoir (33) into the fluid flow area of each spindle rotor. For this warm fluid reservoir (33), a partial flow of the cooling fluid is diverted without cooling during operation and "stays warm" in place, or selectively generated by the electric heat generated therein. Heated.

Comparing the currently determined value with the previous value to make the Tribivari system operate optimally (ie avoid collisions and at the same time provide the best efficacy), identify trends and enable predictions Is very important.
^{* °° *} Extrapolation and interpolation can later ^{avoid the} use of warm fluids if the process of drawing conclusions is adequately backed up by sufficient experience. Nevertheless, warm fluids may help to create defined temperature conditions.

3) k ₀ speed measurement:
The k ₀ velocity measurement, instantaneous compression of the spindle compressor is tested integrally, changes algorithms especially control device, in terms of recognition of compatibility and trends PartCool, it is evaluated.

  Within TribariCU Intelligence, measure the compression ratio of the compressor at zero flow for different rotor speeds for the following purposes (ie, only "suppress" internal leaks and do not discharge media at the outlet).

The actual compression quality level obtained is used as the basis for the continuous comparisons made during operation, the control group stored in the CU of the system itself and OK approval (ie, within the desired tolerance) , The tendency is identified, and prediction is performed by extrapolation.

Perform a self-diagnosis during operation to identify changes (e.g., caused by wear, wear, fouling, deposit formation, operational changes in the process and / or environment, etc.).

Preferably, the k ₀ speed measurement can be combined with the total pressure difference measurement combined with back cooling as a continuous operation test to safely perform collision avoidance using extrapolation.

k ₀ speed measurement of the procedure:
If the inlet pressure for the different rotor speeds at the closed outlet is known, the resulting outlet (excess) pressure is measured by PartCool under "defined temperature conditions" (description = see above) and since k ₀ speed value is determined for the rotor speed is given by the quotient of the outlet pressure, in the form of a numerical table, or given, for example, as a function expressed as follows.
y-axis = _{k 0} value x-axis as the quotient _p a / _{p i} = rotational speed _{n R}

By ^{**** CU} intelligence, temperature conditions, as well as the gap value by thermal expansion of the components of all the working space, because it can selectively adjustable and controlled by PartCool, compression quality levels individually for k ₀ velocimetry Judged by the defined component temperatures, the current as well as the change can be determined by comparing the operating basic output reference value and other measured values, ie by self-diagnosis and prediction and trends (by extrapolation) .

  Further, a safety margin sufficient for performing collision avoidance is determined by performing back cooling with respect to the above-mentioned operation limit.

  In other words, reliable collision avoidance and most efficient compression can both be achieved.

Changes in the useful life of the compressor are detected by repeatedly applying k ₀ speed measurement and back cooling during operation.

4) Integrated pressure difference measurement (hereinafter abbreviated as “ΣΔp measurement”):
At the time of 測定 Δp measurement, set the overpressure selected in the “regular temperature condition” of the outlet collection chamber (12) with the inlet open and the outlet closed, and rotate the spindle rotor very slowly (for example, 10 rotations). / Min) to measure the current flow resistance of the Trivivari compressor stage by measuring the pressure drop in the outlet collection chamber (12) for a selected period of time (eg, 3 minutes). Individual ΣΔp measurements are first made at the end of assembly of each air-end spindle compressor and stored in the CU as “ base reference values ”. In use during operation, while operation is suspended, the 応 じ Δp measurement is repeated according to the selected periodicity controlled by the CU and compared to both the base reference value and all subsequent measurements. You. This allows predictions and trends to be estimated by extrapolation.

5) Comparison of algorithm measurements:
In operation, the CU (25) has a large number of measurements, regulatory actions and responses, and various ratings. Based on previously performed simulation calculations, as well as (FEM) model calculations of the relevant compressor components, an ever-growing database is built, and the building of the database continues with the constantly coming of data. At the CU (25), these data are then continuously compared with each other and interpolated using an algorithm, which is not exactly the same as what is currently occurring (eg, hot carrier gas inlet temperature). The use case is also mapped ("modeled") and stored so that the CU (25) sends the appropriate output signal (32.e).

  Because the amount of data is initially small, the degree of uncertainty is initially rough and obscured by comparisons and interpolations, but the individual (rather specific) databases steadily grow in the CU. As the obscuration decreases, the machine improves and performance increases.

6) Confirmation of the Δφ rotor pair: Δφ is the rotation angle between the spindle rotors. The exact rotation angle play is measured, the result is compared with both the base reference value obtained at the time of assembly and the measurement value obtained later, and the tendency is determined. When using a rotation angle sensor (20 and 21) of each shaft strand, which identifies and evaluates in the sense of providing a prediction, the verification of the Δφ rotor pair by synchronization of the electronic motor pair-spindle rotor, The clearance state Δ3.2 between the spindle rotors (2 and 3) is checked individually for each Tribivali system.

procedure:
In synchronization between the electronic motor pair and the spindle rotor, one motor string (i.e., each spindle rotor with a carrier shaft fixedly connected to the drive motor rotor shaft) is electrically disconnected (and thereby fixed). And) the other motor string confirms the remaining rotation angle Δφ as “remaining rotation angle play” and the value is recorded. The measurement is repeated a number of times for the entire spindle rotor pairing, the maximum and minimum values are recorded, compared again (compared with the base reference value and the subsequently obtained measurements), and the electronic motor pair-spindle The average value is set as the set value specification of the operation by the synchronization between the rotors (if the value is correct, that is, within the recorded allowable range), using the synchronization between the electronic motor pair and the spindle rotor, below,
> Judgment of the formation of deposits or dirt from the decrease in rotation angle play,
> By determining the wear or surface wear and wear from the increased angular play, the appropriate feedback from the CU to a higher level maintenance service station can make a determination on the spindle rotor pair.

7) Combination and evaluation:
The (self) diagnostic tools described above are not only used individually and evaluated, but may also be used in particular in combination. For example, back-cooling need not be performed until the first contact of the components of the working space as a confirmation of the post-rotational limit (and for the risk of surface damage) in the following respects: That is, on the one hand, post-rotation is ensured by the CU pre-defined back-cooling ΔT _BT value (ie the well-defined temperature level of the working space component), and on the other hand, the ΣΔp measurement and / or Or a k ₀ velocity measurement is taken, after which the values determined by these methods are compared with basic reference and comparative values suitable for back cooling and recorded in the CU.

  The following adjustment tools belong to Trivivari Intelligence (as an example).

A) “PartCool” (also called “PartCool & Control”):
The most important adjustment tools are the individual control and adjustment of the cooling fluid flow for each component, with respect to the associated amount of cooling fluid flow (mass flow) and the cooling fluid temperature. This is not a control of "high contrast", but rather a control or adjustment performed by the system response that directly affects the mentioned PartCool parameter, namely the more detailed name "PartCool &Control". Although virtually all changes in the Tribvari system, and processes and environments, can be compensated for by PartCool & Control, this is the data stored in the CU for a particular operating process (extrapolation or interpolation of directly available data). And the resulting gap value, including the corresponding internal gap leakage value, etc., allows the corresponding compression behavior of the Tribivari system to be appropriately adapted to the respective situation. Because.

B) Conformity of π _i :
As each operating process experiences various conditions (eg, with respect to pressure and temperature values, deposition flow rates, ambient conditions, etc.), adjustments to the compression process become desirable for the desired minimum compression energy requirements. This adjustment includes the “internal compression ratio” as the internal π _i value of the compressor, and initially merely geometrically represents the ratio of the inlet chamber volume to the outlet chamber volume. The actual compression ratio (especially the ratio of temperature and heat dissipation during compression) results in known over and under compression, so that such compression must first be minimized as much as possible. The control device of the Tribivali system according to the invention can ideally adjust the current internal pressure ratio at any time by adjusting the partial gas flow through the auxiliary partial outlet opening (15). The implemented adjustment tool is called “π _i adjustment”.

C) FU speed change:
Using this typical and previously known method, the FU (frequency converter) adapts the spindle rotor speed to specific conditions, especially with regard to the currently desired carrier medium volume flow. Volume flow, as is known, is approximately proportional to rotor speed.

D) "ActionStep-ReactionCheck":
Controller by that is induced at selected intervals (e.g., several minutes) is performed, such as in the compressor housing working space configuration flow of the cooling medium for the element and / or [pi _i adjustments such, small changes continuously Brought to you. What is important is to constantly monitor the ΔT _BT value stored in the CU for safe collision avoidance (important!). Based on continuously acquired measurements (especially temperature values), the CU's algorithm can determine if such changes have improved or degraded the current compression process. In particular, it can be determined by energy consumption (ie, engine torque and engine speed, and / or motor current consumption only).

  Thus, {ActionStep-ReactionCheck} is a persistent self-learning and iterative method, and the system response is also to draw conclusions about the current situation of the Tribivali system, so that both functions of the (self) diagnostic tool and the adjustment tool are used. Can be considered as having.

E) Combination and evaluation:
Each of the adjustment tools described above is not only used and evaluated individually, but in particular may be used in combination. Thus, for example, the π _i adaptation by PartCool & Control and the algorithm of the CU itself is performed in a constantly adjusted manner, preferably by evaluation and combination by the ActionStep-ReactionCheck. By recording the results in the CU's own database, the knowledge of the Tribivari system is constantly increased and part of the Tribivari intelligence is built.

  In the case of Trivivari intelligence, the evaluation of the measurements performed is an important prerequisite in making the above adjustments.

  The evaluation is performed according to the following characteristics:

  Here, “synchronization between the electronic motor pair and the spindle rotor” is abbreviated as “ES”.

  For example, regarding "ActionStep-ReactionCheck":

If at the point of application of the current pressure p _B the required power (also confirmed in the ES of each rotor) drops at a known speed or is at a minimum, the gap leakage and entropy balance are simulated and continued. It is possible to define the compression efficiency by evaluating in the CU algorithm through feedback of the temperature value (32.e) by a practical learning (memory of “experience” of the machine). This is hereafter referred to as the subject of an efficient compression process in the current situation.

  Measuring the volumetric flow rate of the conveyed medium is generally quite time-consuming, but is better facilitated when the measurement is performed or is feasible.

  Of course, it is also possible to watch the deterioration rather than the improvement of the compression behavior, in which case an evaluation by the control unit can start an appropriate standard measurement (particularly by PartCool & Control, etc.).

  Advantageously, the flow of the cooling fluid can be controlled in a manner specific to the particular situation, in a manner specific to the application, based on current experience, flexibly by searching for the relevant optimal conditions according to an algorithm stored in the CU. In this case, however, a sufficient external heat exchanger allows for sufficient heat dissipation, in particular with the aid of an advantageous temperature difference. This is the new Tribivali intelligence according to the present invention, which cannot be easily realized from the prior art.

  The Tribivali system actually knows at any time what state each is currently (e.g., in terms of fouling, sediment formation, wear conditions, load capacity, temperature levels, current gap values and compressibility, etc.) Knowing what state it is in, and using that knowledge, a particular actuation process in the current state (!) (Optimal in the sense of the most efficient compression in the current state (!)) Can be performed optimally.

  In addition, through the analysis of the trends and projections described above, the CU can move its situation to a high level of service and maintenance position at the appropriate time to permanently assure system maintenance, protection, maintenance and service and availability. .

  The Trivivari system performs self-learning under specific process conditions, continuously updating the analytical data for each individual CU, optimizing the data using the ActionStep-ReactionCheck, and storing it in the CU's own database. Designed.

CU Intelligence Command Values :
(!) = Important (-) = Insignificant 1) (!) Flow of cooling fluid to 2t rotor (depending on speed of cooling fluid delivery pump or adjustment member of rotor itself)
2) (!) Flow of cooling fluid to the 3t rotor (depending on the speed of the cooling fluid delivery pump or the adjusting member of the rotor itself)
3) (!) The flow of the cooling fluid to the housing can be measured for each section (especially, for example, a large machine of> 75 kW)
4) Cooling fluid flow to the (-) side (actually only the outlet side)
5) (-) Cooling fluid flow to lubricant (no longer electronically synchronized)
6) (!) Rotor speed (by FU (frequency converter))
Possible without slip = synchronous motor 7) (!) Auxiliary partial outlet opening as variable partial gas flow.

Measurement variables:
a) Substantially all temperatures In particular, substantially all temperature differences ΔT with respect to each cooling fluid flow, and the carrier gas and lubricant temperatures, and the component temperatures.
b) Rotor speed
c) Torque for each rotor (electronically synchronized)
d) Each cooling fluid mass flow rate (using at least the selectively adjusted speed / accurate characteristics of the cooling fluid delivery pump) ΔT, at each point in time, Heat dissipation.

Special features:
1) The actual gap values Δ2.1 and Δ3.1 and Δ3.2 are detected during assembly of the compressor individually for each machine, for example, by “back-cooling” or “contact and withdrawal” and stored in the CU. These values are then matched during operation with the CU's algorithm to adjust the various cooling fluid flows of each working space component so that, on the one hand, collisions (i.e., clearance reduction) are reduced. It can be reliably avoided (e.g., depending on the size of the machine with a safety reserve of about 15%), while on the other hand the gap value is a certain maximum value (e.g. about 1 .0 of the cold gap value recorded from the time of assembly). 5 times the value according to the size of the machine).

  This is because the CU always keeps track of the compressor state by managing the temperature state and thermal expansion behavior of the working space components stored in the CU.

2) Self-diagnosis and prediction Judgment, recording and evaluation of the current state, especially by electronic synchronization with speed fluctuations.

3) Process adjustment, ambient environment adjustment, temperature control, and compression adjustment using auxiliary partial exit openings.

4) corresponding to the current (i.e., current state) _{k 0} velocity measurement in combination with reverse cooling of determining the target PartCool containing individual PartCool & Control.

Definition of “working space”: space between inlet (11) and outlet (12) The working space is a pair of spindle rotors (2 and 3) and a small gap value Δxy between various components (less than 0.1 mm) ), And the surrounding compressor housing (1).

  In the working space, the desired compression of the transport medium is performed by the components of the working space, namely the spindle rotor pair (2 and 3) and the compressor housing (1).

  Further, according to the present invention, the CU which is the control device (25) not only monitors, adjusts, and optimally manages the above-mentioned spindle compressor, but also performs the industrial control device in the “process management technology” on the user side. As well as communicating with the entire system / plant controller using automation technology (eg a Profibus system), but also comprising, for example, individual compressor systems with their own CU (25) in each case (at least the user concerned) Actively participate in managing / adjusting the load management of the entire system, for example, to avoid costly current peaks. This belongs to the item “Industry-4.0”. It also contains (preferably if the user agrees) further predictions with appropriate maintenance suggestions for known diagnostic systems (e.g. vibration sensors, temperature profiles, etc.) with corresponding evaluations (software) at the same time. , The feedback to the supplier (or, in the case of more than one, a plurality of suppliers) about the current state of the compressor system with all the individual systems. In addition, for example, process conditions that have been changed or changed by external environmental conditions such as temperature levels (eg, a warmer or cooler environment), another desired pressure level, other than deposit formation, fouling, abrasion, etc. Also included is a constant and continuous adaptation, whereby the intelligent CU system (25) allows the proper adjustment of the cooling water volume, equalization of the internal compression ratio through the auxiliary partial outlet opening (15), and Respond using all means for self-diagnosis to determine the current condition of the compressor in the application, take appropriate corrective action, from adjusting the cooling fluid volume to alerting the operator, and taking other corrective actions. Make predictions.

In the figure, a single point is inserted as an index instead of a subscript. F2 means _RF2, and in the figure, represents the root diameter of the two-toothed spindle rotor.
F = profile root K = profile head C = cooling WK = pitch circle 2 = 2 toothed spindle rotor 3 = 3 toothed spindle rotor

FIG. 1 shows a volume with a rotor geometry according to the invention, comprising a cylindrical evaporator cooling hole (6) according to the invention and adapted to a load-bearing root base body (32) based on the example of a 2t rotor. Fig. 3 shows a two-tooth spindle rotor (2) of longitudinal cross section with a mold root base wall thickness w, from a cylindrical evaporator cooling hole (6) to a plurality of transverse holes (balancing with the required cross section Σ) with the following radii: Detailing the steam outlet (14) having a value;
_RW2 < _RD2 < _RC2
Preferably, for a profile pair without blowholes, the gas carrying "male thread" (31) on the two-toothed spindle rotor is located above the pitch loop. As is known, the drive motor (18) comprises a motor rotor (mounted on the carrier shaft 4 for co-rotation) and a motor stator having an electric stator motor winding (shown as shaded squares). Consisting of an assembly-optionally withdrawing to a vacuum pump (29), if necessary, is initiated in the intermediate chamber (13) of the working space bushing to protect the bearing from the transport medium.

  FIG. 2 shows, for example, a cooling circuit with a bypass of the t0 cooling fluid (9) coming from the circuit, the cooling circuit including a cooling fluid injection (33) into the compressor working space per working point, The iV value due to the steam outlet (14) for each component, i.e. the auxiliary part outlet opening (15) with the housing (1) and the rotor pair (2 and 3) shown in the inlet space (11) Includes target adjustment of compressor volume ratio. Also, the expansion valve shown in the figure can be replaced by a simple height difference, preferably using gravity as the "hydrostatic pressure difference" when steam is the circulating medium (thus, the figure shows that gravity Should adapt to the direction of force).

  The control unit (25) receives and processes, in particular, the various signals obtained from the compressor according to the invention, in particular the current operating requirements, the entire circulation system and, in particular, for each operating point, an adjusting element (38). The adjustment of the compressor components makes it possible to fulfill the above requirements in the best possible way--only the control unit (25) ensures that the system operation can be carried out efficiently (in fact, "new intelligence" Do)).

  With reference to PCT / EP2015 / 062376, the present invention is similar, but now improved by the features of the present invention, to satisfy the steam requirements.

  FIG. 3 shows, by way of example, an end face section of a spindle rotor pair in which the adaptation of the μ (z) values in the direction of the longitudinal axis of the rotor is simplified as a projection in a common plane, in which the axes of rotation of the rotors are at an angle α to one another. And should be shown three-dimensionally for the various positions E, S, V and L in FIG. 5, and for the μ (z) value the following can be said.

R _K2 (z) = μ ₂ (z) · a (z) and R _K3 (z) = μ ₃ (z) · a (z).

  The adaptation of the μ (z) values of the rotor pairs according to the invention, preferably as 3: 2 pairs, fulfills the following three core tasks.

・ Maximization of the nominal pump capacity (based on the cross-sectional area of the rotor pair, the largest possible depression area is achieved)

・ Blowhole-free rotor pair (minimizing internal leakage)

・ The critical bending speed of each spindle rotor is optimally used according to each speed.

design:
Different cooling hole Φ values R _C2 and R _C3 are used for the 2t rotor and the 3t rotor, respectively. Here, the supporting steel shaft is not shown for simplicity, but since the different head strength distributions have a root angle γ _F2 of <90 °, the tooth section of the two-tooth spindle rotor (2) has a minimum head width b _K2. (E.g., 5 mm) without becoming thinner.

  This is done so that the critical bending speeds (i.e., 2t and 3t) for each rotor match, so that for the spindle rotor pair, the following is achieved.

・ Because the rotor pair has no blow holes, internal leakage is reduced.

-Based on the cross-section of the rotor pair shown, the design can achieve a considerably large dimple area, thereby increasing the pumping capacity compared to the cross-section required for vapor compression.

-The two-tooth spindle rotor thus provides heat dissipation during compression with large cooling holes, so that the thermal balance of the components is improved with respect to heat absorption and heat dissipation.

The 2t rotor speed is 1.5 times faster than the 3t rotor, so the two-tooth spindle rotor must rotate faster, so it must be designed according to the present invention at a larger critical bending speed limit, It is advantageous according to the invention to increase the bending speed and to achieve a stiffer shaft, since R _F2 > R _F3 at reduced mass (γ ₀ > 90 °).

-Therefore, a 3t rotor with a low speed has a low bending stiffness, so that a critical bending speed is low, and as a result, rotation is slow.

☆ According to the present invention, the rotor pair is designed such that the critical bending speed of the 2t rotor is 1.5 times faster than the critical bending speed of the 3t rotor, and the following is required. It is the square root of hardness.

However,

FIG. 4 shows an example similar to the example shown in FIG. 1, but in the case of a 3t rotor having a profile-carrying external thread area below the pitch annular line (37), the displacement profile area is the profile tooth and interdental area. A male thread (31) is provided which has various working chambers as a series connection between the inlet and the outlet , ensuring blow-hole-free compression below the pitch loop (37).

  FIG. 5 shows by way of example the rotor pairs obtained in FIGS. 1 and 3 and shows the overall rotor geometry of the rotor, representing the intersection angle α, and the spindle rotors engaging one another in the center. Paired with the engaging lens area.

  FIG. 6 shows a total of four CAD diagrams as an example.

6.a) Compressor housing (1) formed as "pot housing":
The internal treatment of the working space from the closed bottom side on the outlet side and the open inlet side

6.b) Rotating unit:
Each spindle rotor has a carrier shaft, bearings, drive motor and measuring system as a fully assembled and balanced unit (40), the unit is ready to be mounted, below with two teeth Only an example of a spindle rotor is shown, but the same applies to a spindle rotor with three teeth, and the cylindrical flat portion (27) at the entrance of the 2t rotor is not shown.

6.c) Assembly and play adjustment:
In both cases, the separator shows details of the important rotor head play on the housing, for example the head play Δ2.1 between the two-tooth spindle rotor and the housing. The final clearance adjustment between the rotor head and the housing is made by a separating plate (26), for example shown as Δ2.1 in FIG. 6c for a two-tooth spindle rotor head.

6.d) Finished machine:
Both rotating units are mounted on frequency converters (22 and 23) including the pot housing and FU controller (24) for each motor. The FU control device (24) communicates with the control device (25) to perform continuous data exchange, and the FU control device is connected to the user process controller.
The motor windings of the two drive motors (18 and 19) are protected from the transport medium by, for example, the motor securing and vacuum protective potting of the winding assembly or by a gap pot between the motor stator and the motor rotor. .

  The internal geometry of the rotor with the cylindrical evaporator cooling holes according to FIGS. 1 to 4 is not included in FIG. 6 because the embodiment is, as described above, the cylindrical evaporator according to FIG. Instead of being applied to the cooling of said evaporator components via the cooling holes (6), it applies to the option with another cooling water flow as a function of the cooling water according to PCT / EP2016 / 077063. This is because, in the embodiment, only the internal rotor cooling shown in FIG. 6 is sufficient, so that the cylindrical internal rotor cooling is unnecessary.

FIG. 6 illustrates the following. That is,
Good and reliable balance adjustment of the rotating unit, especially for the desired high speed realized with steam up to about 350 m / s as the maximum rotor head speed

◆ Easy installation as a modular system due to different rotor pair variables in the same housing geometry

◆ Make the desired play adjustment by the separating plate (26) to make certain crossover situations (all manufacturing parts are caused by unavoidable manufacturing tolerances "individual" (as accurate as possible for these various components) Compensation is possible due to deviation / dimension differences within intersections)

◆ Electronic-Synchronization by (18) and (19) which are the driving devices of each rotating unit

◆ Intelligent cooling of components using μC as a controller (as described above).

FIG. 7 shows the improvement in the present invention, for example, by a prior art = turbo based operating / working point (Excel), ie a high ΔT due to heat dissipation of t _C.

For heat dissipation below tC, a higher T is desirable.
= Not possible with one of the current turbos (already operating in two stages) = requires a positive displacement machine to provide a p / p pressure ratio = at the same time, always absolute / complete dry operation on steam Must be configured as a machine.

FIG. 8 shows, for example, the pressure-enthalpy graph compression process in vapor compression, showing the improvement due to strong evaporator heat dissipation during compression .
-The conventional technology is shown as a dashed line (with a label)
The improvement according to the invention is shown as a dashed line (labeled),
Compressed from [1] to [2].

Purpose of disclosure:
In comparison with the improvement according to the present invention referred to herein as "HydroCom" (abbreviated HC), the prior art represented by turbos needs to be operated in two stages with intermediate cooling.

Description of the prior art:
When performing isentropic compression (Carnot) from 8 mbar (t ₀ = 4 ° C.) to 48 mbar (t _c = 32 ° C.), intermediate cooling is essential in a two-stage turbo. This is because if the temperature is already 8 mbar to 48 mbar isentropically, the temperature should have risen from 4 ° C. to about 200 ° C. at that time if the intermediate cooling is not performed.

Improvements according to the invention:
For large p / p pressure conditions with high iso-entry compression index, it is necessary to ensure the best heat dissipation during compression, otherwise the compression temperature (in the sense of increased compressor power) Having risen to a lethal height, and according to FIG. 8, the compression actually takes place almost at the dew point line (ie better than isentropy) and the cooling fluid flows (9.2 and 9.3) from being diverted, lowered or overall efficiency somewhat in the cooling technology by the rotor pair cooling effect on the t _0.

  Thus, according to the present invention, HC is a strong requirement according to FIG. 7 in that improved HC works between 7 mbar = 2 ° C. and 96 mbar = 45 ° C. due to efficient heat dissipation during compression. Meet the profile.

  FIG. 9 shows, for example, a table created by Excel showing an example of parameter values of positions E, S, V and L in the rotor longitudinal axis direction of a pair of spindle rotors having individual values for each spindle rotor, and the output described in FIG. The specifications are maximal and constitute only provisional reference values. Of course, both the selection of the designated location and the selection of other parameter values for the particular requirement profile for a particular application need to be made.

  Therefore, it is again emphasized here that this is merely an example and merely illustrates one of the various possible design options of the rotor-pair design according to the present invention.

  In some applications, the cylindrical evaporator cooling holes (6) are designed in a multi-stage cylindrical shape, such as a so-called "step", and it may be advantageous to have an overflow edge, for example, as shown in FIG. .

  When the cooling fluid is mentioned in the specification in general, it refers to the R718 cooling fluid known in the field of cooling, constituted by the negative pressure selected as steam in the positive displacement machine according to the invention or by evaporation It is naturally compressed in fluid form as a cooling fluid (9) for cooling the element.

  The terms “substantially”, “preferably” and “such as” and “if possible” etc., which are interpreted as ambiguous, are ± 5%, preferably ± 2%, especially ± 1%, of the normal value. It should be understood that deviations can be provided. Applicant may disclose any features and sub-features obtained from the claims and / or any features and sub-features obtained in any form from statements in the specification. The right to combine with other features, sub-features, and partial features is reserved even if it exceeds the features of the above.

  In the various drawings, parts having similar functions are always denoted by the same reference numerals, and the description of each will normally be given only once.

Combining refrigerant R744 as CO ₂ (as a two-stage approach, also known as “cascade”) is advantageous at lower temperature values (eg, deep refrigeration) because the minimum temperature of the vapor is above 0 ° C.

  The present invention relates to both clockwise and counterclockwise (Carnot) circulation processes, and relates to vapor compression in cooling, air conditioning and heat pump technology. In order to simultaneously improve the effectiveness and operating behavior over a wide pressure range, the present invention proposes a dry two-shaft positive displacement machine as a spindle compressor, in which the rotor pairs of the spindle rotors (2 and 3) of the machine are arranged. The center-to-center distance is at least 10% greater on the inlet side (11) than on the outlet side (12), the machine is driven by synchronization between the electronic motor pair (18 + 19) -spindle rotor (2 + 3), Internal cooling is applied and the intersection angle α between the two rotor rotation axes is configured in combination with the corresponding μ (z) value in the rotor longitudinal direction to reduce the minimum wall thickness w in the support base body (32). A preferably cylindrical evaporator cooling hole (6) is formed for each spindle rotor, and the (preferably) blowholeless profile thread of the external gas carrying thread (31) is provided. While considering the bearing and the critical bending speed "suitable for the particular spindle rotor", the internal volume ratio is given as an iV value and the internal volume ratio is adjusted during operation by means of an auxiliary partial outlet opening (15), 2 In the case of a toothed spindle rotor, the external gas carrying thread (31) is preferably formed with a cylindrical flat (27) in the inlet area.

1. Compressor housing : provided with an outer cooling area, the distance of the inlet side of the spindle rotor receiving hole being greater than the outlet side, these hole axes preferably according to (9.1a) and (9.1b), for example The cooling fluid flow traverses (i.e. at zero vertical distance) or crosses the external cooling fins in some area along the rotor longitudinal axis, preferably for a cooling fluid flow (9.1) controlled by the controller (25). To obtain a longer rotor length (e.g., diagonally), a plurality of cooling fluid flow areas are formed in the compressor housing, the compressor housing preferably being in accordance with FIG. 6a. And a so-called pot housing.

2. Spindle rotor: preferably made from an aluminum alloy with two toothed gas carrying male threads (31) (abbreviated " 2t rotor ") and preferably with good thermal conductivity (preferably greater than 150 W / m / K) , Fixed to perform co-rotation by a support point (7) on a steel shaft (4) and having a cylindrical evaporator cooling hole (6) of radius _RC2 inside.

3. Spindle rotor: preferably made from an aluminum alloy with 3 toothed gas carrying male threads (31) (abbreviated as " 3t rotor ") and preferably with good thermal conductivity (preferably above 150 W / m / K) , Fixed for co-rotation by a support point (7) on a steel shaft (4) and having a cylindrical evaporator cooling hole (6) of radius _RC3 inside.

4.2t rotor carrier shaft: connected to 2t rotor in the radial _{R W2} (preferably been pressed), the central shaft of the cooling fluid supply hole (4.a) and integrally, and at the same time 2t drive motor (18) It is preferable to rotate with it.

5.3t rotor carrier shaft: 3t are connected to the rotor in the radial _{R W3} (preferably being pressed), and integrally central cooling fluid supply hole (5.a), the same time 3t shaft of the drive motor (19) It is preferable to rotate with it.

6. Cylindrical evaporator cooling holes: corresponding has a radius R _c and the length L _c with respect to the spindle rotor, preferably a cooling fluid guide groove (16), the cooling fluid distributor overflow groove (17) and the support point (7) Having.

7. Support point: The rotationally fixed contact point between the spindle rotor (2 and 3) and the carrier shaft (4 and 5).

8. Synchronous teeth of the spindle rotor pair: In the case of electronic synchronization, in the event of an emergency such as a power failure, for example, the motor also rotates as a fallback transmission, so that the motor automatically switches to generating operation and only at the end (no longer the motor itself). Since power generation is not sufficient), the transmission suppresses contact with the spindle rotor.

  In the case of a fallback transmission, no lubricating oil is required and the tooth overlap is achieved with an increasing overlap ratio (i.e., a larger tooth bevel angle), so that the profile overlap reduces the small slippage in tooth engagement. This can be reduced by reducing the height of the teeth by dynamic movement, which reduces friction and reduces wear, but the sides of the teeth still accommodate the dry running cover as a protection Is preferred.

9. Cooling fluid flow: for cooling the compressor working space components, i.e. the rotor pair and the housing, which are diverted from the circulating medium (34) according to the example of FIG. 2 or schematically shown in FIG. 6d. Any of the other cooling fluid streams, for example, the following applies:

9.1. The cooling fluid flow to the compressor housing can be split as the length of the rotor increases (eg,> 500 mm) as follows.
9.1a Cooling fluid flow through one part of the compressor housing (e.g. the housing outlet side) 9.1b Cooling fluid flow through another part of the compressor housing (e.g. the central region) 9.2.2t to rotor Cooling fluid flow 9.3.3t Cooling fluid flow for rotor

10. Spindle rotor fixed bearing: Receives gas pressure axial force, and accurately fixes each spindle rotor in the longitudinal axis direction.

11. Carrier gas inlet collection space: conveying medium having a gas pressure p ₀ (for simplicity, the pressure loss in the line will be ignored initially).

12. Delivery gas outlet collecting space: conveying medium having a gas pressure p ₀ (for simplicity, the pressure loss in the line will be ignored initially).

13. Intermediate collection / buffer space: preferably provided for each working space shaft path, including for example a gas pressure reduced with respect to the system pressure generated by the vacuum / vacuum pump.

14． Vapor outlet: As a plurality of transverse holes are formed behind the stage having a radius R _D2 or R _D3 each rotor.

15. Auxiliary partial outlet opening: a partial flow medium outlet partial gas flow with an adjusting member (pressure differential valve) for adjusting the internal volume ratio.

16. Cooling fluid guide groove: the groove base surface preferably has a radius _RC for each cylindrical evaporator cooling hole (6) having an inclination angle １７０ 170 ° ≤ ψ 180 °, as indicated in (31) The thread has the largest possible pitch.

17． Cooling fluid distributor overflow groove (small cross section): preferably provided at the groove bottom of (16).

18.2t drive motor: serves as a direct drive for the 2t rotor and is preferably incorporated as a synchronous motor.

19.3t drive motor: serves as a direct drive for the 3t rotor, and is preferably incorporated as a synchronous motor.

20. Rotary encoder: measures the exact rotational angular position of the 2t rotor carrier shaft (4) of the motor.

21. Rotary encoder: measures the exact rotational angular position of the 3t rotor carrier shaft (5) of the motor.

22. Frequency converter: For 2t drive motor (18). This is referred to as “FU.2”.

23. Frequency converter: For 3t drive motor (19). Called "FU.3".

24. FU control unit: Expressed as FU-CU. FU. 2 (22) and FU. Compatible with both 3 (23). The operation data is exchanged directly with the control device (25).

25. Controller (CU): for intelligent operation of the spindle compressor, preferably using links and data stored in the CU memory, as well as measured values obtained later and clearance values from previous simulations, verifications and continuous experience; It functions as a control and regulation device with the evaluation of the current measurement value and the output of the regulation signal based on it, in addition to the FU-CU (24), the user side with the process control technology of the application system, and "Industry 4.0" Connected to the factory control in the sense of.

26. Distance / spacer plate: The rotor is a spindle rotor which is preferably incorporated as a "separator plate" and adjusts the target gap value as a Δ2.1 value for the 2t rotor (2) or as a Δ3.1 value for the 3t rotor (3). It is fixed individually in the longitudinal direction.

27. Cylindrical flat portion (dimension specification “cyl.” In FIG. 2): A portion in a range R _KE2 on the rotor inlet side of the two-tooth spindle rotor (2).

28. Circulating medium: flows through the evaporator (35) (as a core task in cooling technology) to absorb heat.

29. Vacuum pump: removes unsuitable gases, generates the vacuum required for the steam cycle, and preferably draws said gases into the intermediate space (13) to protect the (rotor) bearings.
30. Reservoir: compensates for water loss.

31. Male gas-carrying thread: preferably having a pair of profile rotors without blowholes and performing the compressor core task, i.e. conveying and compressing gaseous carrier media from inlet (11) to outlet (12).

32. Support base base body: Each spindle rotor (2 and 3) has a wall thickness w.

33. Injection of cooling fluid into the working space of the compressor

34. Circulating medium: A heat output through the condenser (36) (as a core task in the heat pump), which is vapor here (circulates under various conditions), but specifically in clockwise and It is also suitable for other circulating media used for both counter-clockwise Carnot processes.

35. Evaporator: Used for circulating media and absorbs large amounts of heat.

36. Condenser: Used for circulating media and outputs a large amount of heat.

37. Above spindle rotor pitch ring (abbreviated as "WK")

38. Regulating member: managed by the controller (25), selectively adapting the volume flow of the cooling fluid stream (9).

39. Vibration sensor: Each time the spindle rotor is internally cooled, a different amount of cooling fluid is used to identify possible changes in the residual imbalance.

40. Rotating unit: provided for each spindle rotor, each in a completely assembled and balanced state, and mainly composed of the following elements.
・ Spindle rotor (2, 3)
・ Carrier shaft (4, 5)
・ Synchronous teeth (8)
Bearings (10)-serve the function of fixed bearings and working space shaft seals, for example having (13).
.Drive motors (18, 19)
-Rotary encoder measurement system (20, 21)-a total of two rotary units (40) are provided for each spindle compressor.

Claims (16)

It operates without a working fluid in the working space to carry and compress a gaseous carrier medium, preferably steam, into a compressor housing (1) having an inlet collection chamber (11) and an outlet collection chamber (12). In a spindle compressor that functions as a two-shaft rotary displacement positive displacement machine including a spindle rotor pair,
The center distance of the pair of spindle rotors at the inlet end is at least 10% greater than the distance at the outlet end, and the two spindle rotors (2, 3) are driven by electric motors (18, 19), respectively. A spindle compressor, wherein the electric motors (18, 19) are controlled by electronic synchronization and the spindle rotors (2, 3) rotate in a non-contact state.   2. The spindle compressor according to claim 1, wherein one spindle rotor (2) has two teeth and the other spindle rotor (3) has three teeth, and the electronic synchronization is between two and three. 3. A spindle compressor according to 3.   3. Spindle compressor according to claim 1 or 2, wherein each said spindle rotor (2 or 3) has an internal cooling means, said means preferably having a radius RC2 or a three-toothed spindle on a two-toothed spindle rotor. A spindle compressor incorporated as a cylindrical evaporator cooling hole (6) having a radius RC3 on the rotor. 4. The spindle compressor according to claim 3, wherein the evaporator cooling holes (6) have the following characteristics:
a) at least one cooling guide groove (16) containing an accurate observation of the Rc value (less than 1% deviation),
a.1) a groove base surface having a tilt angle 170 ° ≦ ψ ≦ 180 ° as f (z), and / or
a.2) comprising an outlet area having a higher thermal conductivity than the inlet-side area;
b) cooling fluid distributor overflow groove (17),
c) support points (7) for non-rotational support of the corresponding carrier shaft (4 or 5),
d) A spindle compressor having an internal structure with at least one, preferably a plurality of, of the steam outlets (14) provided in the inlet chamber (11).   A spindle compressor according to any one of the preceding claims, wherein each spindle rotor system is incorporated with a balanced rotating unit (40) in the assembled state, preferably provided with a separating plate (26). Is a spindle compressor characterized by finally setting a play between a rotor head and a housing.   The spindle compressor according to any of the preceding claims, wherein at least one vibration sensor (39) is provided, the sensor being connected to a control device (25), wherein the control device (25) comprises a cooling fluid. Spindle compressor characterized in that the supply of stream (9) is limited to an amount that maximizes overall efficiency.   7. The spindle compressor according to claim 2, wherein the critical bending speed of the two-tooth spindle rotor is about 1.5 times the critical bending speed of the three-tooth spindle rotor (3). 8. A spindle compressor characterized by being high (preferably with a tolerance of less than ± 30%). The spindle compressor according to any one of the preceding claims,
The intersection angle α between the axes of rotation of the two spindle rotors, combined with the corresponding μ (z) values in the longitudinal direction of the rotor, gives each rotor a minimum (ie, a specific tooth height for material strength). Cylindrical evaporator cooling holes (6) with suitable (wall thickness) w provide a (preferably) blowhole-free profile of the gas carrying male thread (31), a critical bending speed "adapted to a particular rotor spindle" and , Formed simultaneously on the support base base body (32) (e.g. by position indications E, S, V and L), taking into account the realization of the iV value of the internal volume ratio (as described above) at the same time, A spindle compressor, characterized in that the external thread (31) has an inlet area formed as a two-toothed spindle rotor (2), preferably a cylindrical flat part (27). The spindle compressor according to any one of the preceding claims,
The temperature conditions for the components of the working space are adjusted as a basic step (as described above) in a manner tailored to the specific application during the heat dissipation of the operating components, in order to avoid play reduction and to avoid excessive play values. Maintaining the play value between the differences (as described above), the FCT phase during the heat dissipation of the components (as described above) in the working space of the compressor, preferably in said inlet collection chamber (11) Perform a cooling fluid injection (33),
・ As a divided cooling fluid flow,
・ As another cooling water flow,
・ By delayed evaporation
A spindle compressor having improved efficiency and all being regulated and controlled by a control device (25). The spindle compressor according to any one of the preceding claims,
Each of the spindle rotors (2, 3) is made of an aluminum alloy and co-rotates by being pressed against a steel shaft at a support point (7), thereby forming only the male gas carrying screw (31), and (2, 3) is a spindle compressor having an already completed internal structure. The spindle compressor according to any one of the preceding claims,
Spindle compressor characterized in that said internal volume ratio is adapted to current operating conditions by means of an auxiliary partial outlet opening (15). The spindle compressor according to any one of the preceding claims,
A spindle compressor, wherein a steam outlet (14) is provided directly at said inlet. The spindle compressor according to any one of the preceding claims,
A cylindrical flat part (27) is provided at the inlet of the two-toothed spindle rotor, in particular, in the case of the two-toothed spindle rotor (2), the gas-conveying external thread (31) has the cylindrical shape at the inlet area. A spindle compressor having a flat portion (27). The spindle compressor according to any one of the preceding claims,
Said two-toothed spindle rotor (2) is provided with an intermediate support, whereby the weight reduction is preferably achieved, especially for bending stiffness and also for a low moment of inertia at start-up (or braking), eg CFRP suitable for vacuum A spindle compressor characterized by being achieved from a fiber composite material in the form of a material. The spindle compressor according to any one of the preceding claims,
At least one cooling fluid supply (9.2 and 9.3) is provided, each spindle rotor having a cylindrical evaporator cooling hole (6), said cooling hole being said cooling fluid supply (9. 2 and 9.3). The spindle compressor according to any one of the preceding claims,
Each drive has a hollow shaft, and cooling fluid supplies (9.2 and 9.3) for the cylindrical evaporator cooling holes (6) of the drive are provided via the hollow shaft and the bearings (10 A) a spindle compressor characterized in that it is also preferably formed as a highly durable bearing, in particular a grease-lubricated hybrid bearing, an all-ceramic bearing or a magnetic bearing.