WO2018134200A1 - Compresseur de vapeur d'eau comportant une machine volumétrique de compression à sec en tant que compresseur à vis - Google Patents

Compresseur de vapeur d'eau comportant une machine volumétrique de compression à sec en tant que compresseur à vis Download PDF

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Publication number
WO2018134200A1
WO2018134200A1 PCT/EP2018/051005 EP2018051005W WO2018134200A1 WO 2018134200 A1 WO2018134200 A1 WO 2018134200A1 EP 2018051005 W EP2018051005 W EP 2018051005W WO 2018134200 A1 WO2018134200 A1 WO 2018134200A1
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WO
WIPO (PCT)
Prior art keywords
spindle
rotor
cooling
cooling fluid
compressor
Prior art date
Application number
PCT/EP2018/051005
Other languages
German (de)
English (en)
Original Assignee
Steffens, Ralf
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE102017000381.5A external-priority patent/DE102017000381A1/de
Priority claimed from DE102017000382.3A external-priority patent/DE102017000382A1/de
Application filed by Steffens, Ralf filed Critical Steffens, Ralf
Priority to EP18701293.5A priority Critical patent/EP3571408A1/fr
Priority to US16/478,216 priority patent/US20200386228A1/en
Priority to JP2019538431A priority patent/JP2020505544A/ja
Priority to CN201880018982.3A priority patent/CN110520626A/zh
Publication of WO2018134200A1 publication Critical patent/WO2018134200A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/54—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
    • F04C18/56—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/54—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
    • F04C18/56—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/565—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing the axes of cooperating members being on the same plane
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C27/009—Shaft sealings specially adapted for pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/025—Lubrication; Lubricant separation using a lubricant pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2220/00—Application
    • F04C2220/10—Vacuum
    • F04C2220/12—Dry running
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • F04C2240/402—Plurality of electronically synchronised motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings

Definitions

  • Circular processes are preferably described according to Carnot with heat dissipation and heat absorption and a compressor as a drive for the circulation medium in the gaseous phase.
  • Circular processes are used very frequently and have become indispensable in our daily lives. These include right- and left-rotating Carnot processes, with desired / targeted heat intake to fulfill a cooling task (in the refrigeration and air conditioning industry) or with desired / targeted heat delivery to fulfill a heating task (keyword "heat pump ”) with heat exchangers for heat absorption and heat release.
  • a drive in the form of a compressor (compressor) for the circulating medium in its gaseous phase is generally required.
  • the circulation medium with its specific properties is crucial.
  • various artificial generally chemically produced such as HFC and HFC
  • natural such as ammonia, propane, propylene, isobutane, ethane cycle media.
  • Non-refractory water is ideal as a circulation medium because of its general availability, it is completely non-toxic, can be safely used at low pressures as water vapor and meets even the most stringent guidelines and safety regulations, is resource-friendly, environmentally friendly, low maintenance, efficient and practically without any risk potential (incombustible, non-explosive, uncritically).
  • the object of the present invention is the compression of (preferably) water vapor in the known working area and pressure range, which is generally referred to as a rough vacuum, by a positive displacement machine with mastery of the respective desired pressure differences and the large p / p pressure conditions with the Displacement machine typically steep characteristic (ie pressure values on volume flow with the corresponding operating points) to accomplish, this machine must be completely dry running (no operating fluid) and should have a total efficiency for the entire system, which is better for the entire application than the Today's turbocompressors, so that the user requirements in refrigeration and heat pumps and other (Carnot) circular processes are better met, especially in terms of a larger pressure range.
  • This object is achieved according to the invention for the compression of water vapor at pressures below atmospheric pressure (preferably between 6 mbar and 300 mbar, ie in the classic vacuum region) in the power range of less than 1 kW to well over 100 kW as refrigeration cycle power for refrigeration (ie industrial refrigeration , Commercial refrigeration and building air conditioning) or as heat pump cycle power [the required compressor power is corresponding to the so-called.
  • COP ( ' e
  • cylindrical evaporator cooling bore (6) as a "rotating cylinder evaporator" for automatic self-cooling cooling by the water to be evaporated as a spindle rotor cooling fluid under the pressure p 0 * and the temperature t 0 * [these values with certain technical deviations, such as pressure drops, temp. increase due to unavoidable heat transfer] is diverted from the circuit of FIG. 2 and in the cylindrical evaporator cooling bore by rotation centrifugal forces in operation inevitably always goes exactly where it is currently most urgent for each operating point is needed, wherein the cylindrical evaporator cooling hole (preferably) has the following features as explained below:
  • a "rotating cylinder evaporator", as the internal cooling of the spindle rotor is designed according to the invention has the best possible heat transfer properties for the present task, because the centrifugal forces consistently the best possible heat transfer is achieved by the heavy liquid parts in the rotating cylindrical evaporator Cooling hole constantly displace the lighter gas components of the heat transfer surfaces to evaporate again immediately, so that thus get the next liquid parts for the heat transfer to the rotor material to the desired heat transfer, and also at the same time still in RotorlNicolsachsraum thanks cylindrical-equal radii values to due to the highest evaporation, there is also the greatest need for heat removal, because there will be different power distribution for each operating point in the rotor longitudinal axis, so that with the known high evaporation enthalpy differences with less (see FIG Values in Fig. 9) cooling fluid supply highly efficient heat dissipation during compression is achieved, so that according to Fig. 8, the compressor line of [T] is advantageously steep and run for the compressor clearly better than isentropic
  • Cylindrical evaporator cooling bore (6) of radius Rc along the length Lc at the spindle rotor displacement profile length LR, said cylindrical evaporator cooling bore preferably beginning between positions E and S in the inlet region and preferably via the outlet end at L, so the values for LR and Lc are comparable (approximately equal).
  • the cylindrical evaporator cooling bore (6) is designed as a so-called “inner structure” preferably via cooling fluid guide grooves (16), cooling fluid distributor overflow grooves (17) and support points (7).
  • the cylindrical evaporator cooling bore (6) should be as exactly cylindrical as possible (ie deviations well below 1%), wherein e.g. Manufacturing tolerances in the Rc values are preferably set such that deviations tend to lead to larger Rc values in the direction of the outlet (ie in the region of the position L).
  • the groove bottom of the cooling fluid guide grooves (16) is preferably designed such that the groove base surfaces are performed with inclination angles ⁇ ( ⁇ ), which is preferably in the range depending on the z-position in Rotorlteilsachsutter, which is commonly referred to as z-axis
  • the cooling fluid guide grooves are preferably designed with a pitch as great as a thread, for example as in the case of the gas delivery external thread (31), in order to be able to do so to implement the task of minimizing the residual imbalance resulting from the introduction of the cooling fluid (9.2 or 9.3) into each rotor (since each fluid collects in the rotating system to the greatest possible distance from the current pivot point and thus reinforces the residual imbalance), which, for example, is very poorly met at zero slope of the cooling fluid guide grooves.
  • This effect of the residual imbalance amplification is inventively used simultaneously to minimize the amount of cooling fluid supplied (9.2 or 9.3) per rotor by vibration sensors (as used for example in the camp monitoring)
  • this residual imbalance gain by an excessive amount of cooling fluid in each rotor system show, thanks to different rotor speeds (the 2z rotor always rotates 1, 5 times faster) is exactly determined in which rotor just the amount of cooling fluid is too high, so that the control unit (25) via the Regulierorgane (38) the current correct (in terms of minimum required cooling fluid) setting can make.
  • cylindrical evaporator cooling bore (6) is of course described here only by way of example with support points (7) and cooling fluid guide grooves (16) with radius Rc and with cooling fluid distributor overflow grooves (17). Of course, other embodiments are also conceivable here.
  • cooling fluid (9) esp. Always limited to the rotors to the minimum amount, possibly even sporadically and impulsively, both to avoid critical imbalances and to minimize the amount of diverted cooling fluid flow (9) in the sense of maximizing the total Efficiency, because this cooling fluid flow (9) the actual circulation medium (28) in the evaporator (35) is missing in the heat absorption.
  • the cylindrical evaporator cooling bore (6) in each spindle rotor thus always receives only so much water (with a technically usual tolerance of, for example, + 1%), as is currently needed for evaporation at the respective operating point.
  • This minimization of thedefluidstrommenge (9) is achieved for example by measurement via known and simple vibration sensors (eg for rolling bearing monitoring) to determine the degree of filling in the respective cylindrical evaporator cooling hole (6) per spindle rotor (2 or 3), because an increased Amount of water in the respective cylindrical evaporator cooling bore (6) will increase the residual imbalance in the rotating system and can, due to different speeds of the spindle rotors (the 2-toothed spindle rotor rotates by a factor of 1, 5 faster than the 3-toothed spindle rotor) as imbalance excitation associated with the respective rotation system of the 2-toothed or 3-toothed spindle rotor so that the respective amount of cooling fluid (9.2 or 9.3) is adjusted accordingly to the minimum amount. So it is supplied only as much water as is currently needed for evaporation in the current operating point.
  • Cooling fluid injection (33) in the working space for selectively influencing the conveying gas temperatures in the working space, ie the space between the inlet (1 1) and outlet collecting space (12).
  • Cooling fluid injection (33) in the working space for selectively influencing the conveying gas temperatures in the working space, ie the space between the inlet (1 1) and outlet collecting space (12).
  • the heat dissipation for the workspace components is to ensure as a basis at all times and to ensure that game consumption (which generally leads to failure of the compressor, so-called "crash") between the work space components is reliably avoided at every operating point:
  • the base stage for component heat dissipation ensure that the play values (ie, the distance values between the workspace components) remain within a certain range, ie, the minimum play values in operation is about 0.03 to 0.09 mm (depending on the size, with large machines with> 150 mm center distance above 0.05 mm), the base stage for component heat dissipation during operation should be designed so that not only the aforementioned Spielaufzehrung is safely avoided (as indispensable mandatory requirement, whereby said minimum play values receive a safety margin of about 20% to 50%), but also the play values for other operating points due to the different thermal expansion behavior of the components compared to these lower play values by a factor of 2 to max.
  • VET compression end temperature
  • the necessary heat dissipation during compression is known to depend on the temperature difference between the gas in this volume and the surrounding heat-dissipating surfaces of the work space components, in addition, the heat transfer coefficient (in water vapor known to be quite high values) and the heat conduction ( therefore, as the material for the spindle rotors, an aluminum alloy is preferably used).
  • the cooler the surfaces of the working space components can be kept above the respective cooling flow, the better is the heat dissipation during compression and the lower the temperature increase of the delivery gas in the funded and compressed working chamber volumes, hence the compressor working line increasingly steeper - shown by way of example according to FIG. 8 between the points [T] and [2].
  • the cooling fluid flow (9) for heat dissipation for the working space components can be represented by the following two approaches:
  • the cooling fluid flow (9) is diverted from the actual circuit as a partial flow, which is considered a preferred solution because it the maximum heat dissipation with the cylindrical evaporator cooling hole (6) during compression allows.
  • the only disadvantage is the fact that this branched cooling fluid stream (9) is withdrawn from the main stream and thus is missing in the fulfillment of the core task in refrigeration, ie the heat absorption in the evaporator (35).
  • this branched cooling fluid partial flow is not lacking the circulation medium (34).
  • the branched cooling fluid flow (9) is cylindrical Evaporator cooling hole (6) to realize as exemplified in Fig. 2, wherein the amount of diverted cooling fluid flow (9) targeted and controlled to the respective requirements profile in the sense that in each situation and regulated by control unit (25) each branched off only as much amount as the cooling fluid flow (9), that the compressor efficiency improvement by the heat dissipation overall energy more advantageous than the disadvantage described above in the additional effort by the branched cooling fluid flow. If this approach is no longer achievable for some applications, then the "separate cooling water flow" described below applies.
  • this cooling fluid (by heating the heat of compression now heated) by Pitot tube (such as in DE 10 2013 009 040.7 or also described in 10 2015 108 790.1) is tapped, it has a higher pressure than pc because of the high kinetic energy and consequently to a point after the compression process, for. B. in the outlet-collecting space (12), the circuit is recycled, where this liquid is then evaporated and this task specific can absorb heat again, the amount of cooling fluid is then adjusted so that the overall efficiency is improved.
  • the correct (in terms of efficiency and imbalance minimization) cooling fluid quantity for the respective operating / operating point of the control unit (25) is regulated, in this control unit, the corresponding data are stored (eg corresponding process simulation) as well as “trial-and-error” as self-learning process, in which the system independently tries out variations and uses the reactions (ie energy demand and power balance) to determine with which setting the highest efficiency is achieved in the respective operating point becomes.
  • This approach can also be called “action”. Therefore, it has to be decided on a case-by-case basis which of these approaches best solves the application-specific task.
  • the inner volume ratio ie the quotient of the working chamber volumes between inlet and outlet
  • the "iV value” must be optimally adapted to the respective operating point in order to avoid damaging over- or under-compaction.
  • the iV value can be adjusted according to the invention by means of additional partial outlet openings (15), but must first be determined via the spindle rotor pair design.
  • the iV value is basically influenced by the following 3 variables:
  • the conveying gas (water vapor) is to be compressed, for example, from 7.0 mbar to 95.9 mbar, resulting in a compression ratio of:
  • Each spindle rotor (ie the aluminum part, which is non-rotatably mounted on the steel shaft) consists of 3 sections: a) External gas supply thread (31)
  • the gas delivery external thread (31) is preferably made only after the rotationally fixed connection with the respective steel shaft in order to minimize the size of the comfortably ground- wall thickness w.
  • R K2 ( z ) ⁇ 2 ( ⁇ ) ⁇ 3 ( ⁇ )
  • R K3 ( z ) ⁇ 3 ( ⁇ ) 3 ( ⁇ )
  • the foot angle ⁇ ⁇ 2 is selected specifically by this particular esbe .
  • ⁇ 2 > 0.6 is performed greater than 90 °, the head cylinder width b K2 ⁇ z) does not fall below a selected limit, eg 5 mm.
  • Position S (can also be represented as a range over several z-values)
  • ⁇ -value preferably such that the inlet working chamber receives the largest possible volume without violating the stated boundary conditions (ie cylindrical evaporator cooling bore, wall thicknesses on the supporting base body (32), blowhole freedom, critical bending speed etc. ), wherein the ⁇ value according to FIG. 3 and the equations given for each z position in the rotor longitudinal axis direction is specifically designed, as shown by way of example in FIG. 9.
  • Position V (can also be represented as a range over several z-values)
  • Position L (can also be represented as a range over a plurality of z-values), preferably as a cylindrical end, which is expediently designed to project beyond the end of the external thread into the outlet space, as shown by way of example in FIG.
  • their preferred specific values are shown by way of example in FIG. 9 for these positions. The emphasis is exemplary, because both other positions and other values can be realized.
  • the parameters mentioned in this Fig. 9 merely show a meaningful embodiment showing the "spirit" of this invention.
  • each position can truly also be implemented as a z-range over several z-values in the rotor longitudinal axis direction and not just as a singular z-position.
  • the crossing angle alpha according to FIG. 5 between the two spindle rotor axes of rotation is carried out in combination with the respective (z) value in rotor longitudinal axis direction such that each rotor has a cylindrical evaporator cooling bore (6) with minimal (ie with respect to the material Firmness to the respective tooth height) wall thickness w on the supporting comfortably ground stresses (32) is formed (for example, according to the above position descriptions of E, S, V and L) while taking into account the (preferably) blowhole-free rotor profile design of the gas delivery external thread (31) and "spindle rotor-specifically matching" (° * °) bending-critical speed according to the following point to the critical bending speed and implementation of the internal volume ratio according to the embodiment previously described.
  • each rotor system according to the invention as a rotation unit (40) running, as it is exemplified in Fig. 6b, of crucial importance, because the balance for the complete rotation unit (40), whereby the balancing quality is improved.
  • the rotor speed results from the maximum permissible rotor head speed below supersonic for the fluid in the work area.
  • the 2-toothed spindle rotor (2) is also flattened cylindrical in the inlet area so as not to hit the rotational speed limit too early in this area, because in the outlet direction the rotor head velocity drops rapidly due to smaller diameter values (see FIG 9 the table values).
  • the bearings are for example / preferably designed as a hybrid spindle bearings (eg type XCB70 ..) sealed on both sides with appropriately adjusted lifetime lubricant and correspondingly far away from the fluid through the working space shaft seals, said working space waves -Abdichtungen next Abscheide- and defense facilities (see ima catalog from the WZ-münbau for spindle seals) still neutral collection / buffer rooms (13) as a protection as well as the unconditional (!) Prevention of any gas flow through the bearing, without exception need a safe bypass, so a gas-permeable bypass (channels, holes) with minimal flow resistance.
  • a hybrid spindle bearings eg type XCB70 ..
  • the evaporator cooling for the work space components can be shown in FIG. 8 as a horizontal line with the pressure p 0 * at t 0 * represent, as exemplified in Figure 2:
  • the * please note, because This pressure may well and specifically differ from the pressure p o at t 0 in the evaporator (35), if it is advantageous according to the application-specific process simulation. It is also possible to perform the evaporator cooling for the work space components via a separate refrigeration cycle.
  • the Control Unit (25) implements the respective application-specific requirements by the control unit (25) manages the entire system and intelligently regulates, controls and monitors. All relevant data are stored in the Control Unit (25) and are collected and evaluated.
  • Tivari The positive displacement machine according to the invention, hereinafter referred to simply as “Tribivari”, is designed as an intelligent system, which is solved by the features and properties described below, where the abbreviation “ES” stands for the “electronic motor pair spindle rotor synchronization” according to the invention.
  • ES electrospray motor pair spindle rotor synchronization
  • a compressor works in principle between the following two limits:
  • PartCool CU intelligent guided cooling water flow per component
  • the CU is used for the specific PartCool regulation thanks to an algorithm with targeted and comparative learning of deviations and differences.
  • Tribivari knows at any time how far its own load can be driven in each case to: a) safely avoid the crash (splitting waste)
  • Tribivari helps itself by repairing itself practically by hand.
  • Tribivari Unlike the currently only "aufgesattelten" (Screws could already work before) controls, the intelligence of Tribivari is a conceptual part of this new compressor technology by the entire operation under any conditions including their constant changes individually (ie specific to each Tribivari with Their very own tolerances and respective operating conditions / deviations) of the control unit with constant self-diagnosis (! and prognosis with constant adjustment to the process under different conditions (colder / hotter environment, worse cooling etc.) is led. This is the novel Tribivari intelligence.
  • oil-injected screws injected oil quantity (it is indispensable due to internal leakage, heat dissipation and lubrication) can not be adjusted arbitrarily with regard to oil quantity and oil temperature.
  • neither of these machines can adjust their internal compression ratio (ie, between over-compression and sub-compression) to the respective operating point (compare refrigerant compressor effort per housing slide).
  • Tribivari is fundamentally superior in that it fulfills 3 characteristics simultaneously:
  • Tribivari dry PLUS eta PLUS ⁇
  • ⁇ comprehensive over cooling fluid mass flow and cooling fluid temperature suitable for any current situation and not only for one operating point, but always optimally for the entire work area
  • Simulation algorithm stored in the CU fed by the individual gap values and the current situation and correspondingly adapted reactions, based on maps that are constantly expanding and interpolated and compared (!) With constant learning.
  • Tribivari helps itself by practically repairing itself Tribivari by hand, ie:
  • Tribivari is so intelligent, by Tribivari with the mentioned (self-) diagnostic tools as so-called. "Self-diagnosis” initially recognizes itself when Tribivari changes due to wear, abrasion, contamination and / or deposit formation, and can then be adjusted from the above-mentioned Regulier tools its operating behavior, concretely this is e.g. at each operating point, as required by the user's process operating point in the particular situation,
  • Tribivari Based on the individual start state of this Tribivari system stored in the Control Unit, the current state (due to wear, abrasion and / or contamination, deposit formation possibly changed) of Tribivari is taken into account in the algorithm of the Control Unit as well as the current ones Ambient conditions (hot, colder, dirty heat exchangers, etc.) and the currently desired operating requirements (ie in terms of volume flow, pressure level, but also allowable power consumption in the sense of avoiding expensive power spraying, etc.).
  • Ambient conditions hot, colder, dirty heat exchangers, etc.
  • the currently desired operating requirements ie in terms of volume flow, pressure level, but also allowable power consumption in the sense of avoiding expensive power spraying, etc.
  • Tribivari uses its own (self-) diagnostic tools, ie, by means of co-rotational speed measurement and / or ⁇ measurement and / or algorithm-measured value comparison and / or ⁇ -
  • Tribivari can determine this via the algorithm in his own control unit, where individual guideline values (stored in the assembly of this tribivari) are available for the different measured values and are stored with the respective links, relationships and interpretations Measured values are compared.
  • Tribivari can not only be operated safely but also in the respectively optimum (in the least energy requirement) range. At least by inverse cooling, it can even be determined individually for each spindle rotor which gap value has decreased, namely ⁇ 2.1 or ⁇ 3.1, in order accordingly to determine the relevant cooling fluid flow 9.2 or 9.3 according to value tables ⁇ e. calculated by FEM simulations).
  • Tribivari determines via its own (self-) diagnostic tools that the gap values have increased in the inlet area, eg due to abrasion / wear, noticeable via worse compression behavior. To compensate for this situation (to "rescue”), for example, the cooling fluid flow to increase 9.1 b at the compressor housing inlet area. Based on “PartCool” as a self-diagnosis using:
  • the co-rotational speed measurement is possibly combined with ⁇ measurement combined with the inverse cooling as an ongoing operational check for safe crash avoidance by means of extrapolation.
  • y-axis ko value as quotient p a / pi
  • the inverse cooling is also executable via CU-deposited algorithm as extrapolation of several "harmless” (in the sense of readily available) hot-fluid temperatures (preferably from the warm fluid reservoir (33), for example).
  • Tribivari intelligence exemplary
  • PartCool also called “PartCool & Control”
  • Tribivari spindle compressor according to the invention at least the temperatures mentioned in Fig. 1 are measured, not only from the cooling fluid but also from the components. This is very easy with the compressor housing and in the frame-fixed inlet and outlet area, because it is stationary (frame-mounted) components.
  • the relationships between cooling fluid temperatures and rotor temperature for the various load states are stored in the control unit (25) via previously performed simulation calculations and model calculations (eg by FEM), so that the "defined temperature - Ratios "for the entire Tribivari spindle compressor in the CU (25) are always known with sufficient accuracy or are to be converted via interpolations (known geometry and material properties) with the resulting individual gap conditions also widely known.
  • the CU has an algorithm for converting to a uniform comparable state, which will henceforth be referred to as a defined temperature ratio.
  • each finished * 0 * spindle rotor is inserted individually into the compressor housing (1) until complete contact with its housing bore as so-called. "Zero-gap" so touching, paying attention to as complete as possible support between the rotor and housing (if necessary. Check by means of Touchierpaste and slightly rotating by hand to secure the rotor-housing contact), which is why the housing is preferably vertical and the spindle rotor of is introduced above.
  • the gap size .DELTA.2.1 and .DELTA.3.1 can thus be set and logged in a targeted manner, which has hitherto not been possible.
  • a constant inclination angle ⁇ 2 or ⁇ 3 is advantageous, but are also stretch conform (ie according to simulation of the compression process and heat dissipation of the working space components) in Rotorlteilsachsraum different angles of inclination possible, which is why then a mean inclination angle can be applied, or that inclination angle which mainly determines the gap dimension ⁇ 2.1 and ⁇ 3.1 according to the simulation of the compression process and the heat dissipation of the working space components.
  • the AT BT values are therefore to be regarded among other things as protection of the crash avoidance as still safe and several times by Inverskühlung examined component temperature differences of the CU in the enterprise always observed and kept, by the AT BT values are not exceeded.
  • the "PartCool" can then be adjusted in such a way that the gap values in each area are optimal: optimal means that on the one hand crash (ie gap wastage) is safely avoided, which is thanks to the knowledge of the respective AT BT values Now finally possible, and on the other hand, the inner gap leakage on the controlled by PartCool gap values according to the present simulation of the compression process is controllable so that the efficiency is maximized for exactly the currently present compression process.
  • the actual start state is recorded specifically for each screw compressor after contact + retraction + fixation of its actual AT BT values as mounting AT BT values and stored in its control unit (25).
  • linked measures are carried out as described under "Combination &Evaluation" and these individual measured values are stored in the CU for this Tribivari compressor. This process forms the reference reference for possible changes (due to wear, abrasion, contamination, deposit formation, etc.) during later operation.
  • the mounting AT BT values are preferably repeated (or similar, in order to allow conclusions about the mounting AT BT values by means of a stored algorithm in the CU * 00 * ) and combined with combination & evaluation the current status of this Tribivari system, so that this Tribivari system is operated optimally between working limits (in terms of efficiency as described).
  • the insert inverse cooling is preferably done during breaks in operation, in which case the higher temperature fluid for the fluid flow areas of each spindle rotor comes from a hot fluid reservoir (33).
  • a hot fluid reservoir (33) either during operation, a cooling fluid partial flow is diverted uncooled and there "warm parked” or selectively heated there by an electric heater generated there.
  • the instantaneous compressibility of this spindle compressor machine is integrally checked, in particular the changes in the algorithm of the control unit being evaluated in the sense of adaptation of the PartCool and recognition of a tendency.
  • the co-rotational speed measurement is possibly combined with total pressure difference measurement combined with inverse cooling as an ongoing operational check for safe crash avoidance by means of extrapolation.
  • y-axis ko value as quotient p a / pi
  • the current flow resistance of the respective Tribivari compressor stage is measured by setting a selected overpressure at "defined temperature ratios" with open inlet and closed outlet in the outlet collecting chamber (12) and with very slowly rotating (eg less than 10 revolutions per minute) spindle rotors the reduction of pressure in the outlet plenum (12) is measured for a selected period of time (eg 3 minutes).
  • This individual ⁇ measurement takes place for the first time at the end of the assembly of each spindle compressor AirEnd and is referred to in the CU as so-called. "Basic reference" deposited.
  • this ⁇ measurement is repeated in the pauses at a selected rhythm controlled by the CU and compared both to the base reference and to all follow-up measurements. From this a prognosis and tendency can be deduced by extrapolation.
  • the CU (25) contains many measured values, regulatory actions and reactions as well as various evaluations. Based on the previously performed simulation calculations as well as (FEM) model calculations of the relevant compressor components, a steadily growing database is created, which is continued with the constantly incoming data. In the CU (25), these data are now constantly compared and interpolated using an algorithm so that they are also mapped ("modeled") and stored for applications that are not exactly as they are currently occurring (for example, higher production gas prices). Inlet temperatures), from which CU (25) the appropriate output signals (32. e) are given.
  • CU for example, to higher-level maintenance and service stations.
  • the (self-) diagnostic tools mentioned are not only to be used individually but also in combination and evaluated.
  • inverse cooling does not have to be driven until the first contact of the workspace components as a check of the still-rotatable limit (also because of the risk of surface damage) by the inverse cooling at an AT BT value previously set in the CU (
  • a clearly defined temperature level of the working space components) on the one hand the rotation is still guaranteed and on the other hand a ⁇ measurement and / or co-rotational speed measurement are performed, the then determined by these methods values are compared with that for this inverse cooling corresponding and stored in the CU base reference and comparison values.
  • Tribivari intelligence exemplary
  • PartCool also as “PartCool & Control”:
  • the most important regulating tool is the individual control and regulation of the cooling fluid flows for each component over the respective quantity (mass flow) of the respective cooling fluid flow as well as over the respective cooling fluid temperatures.
  • This is not a "stubborn" control, but a regulation or regulation in that the system response has a direct influence on the mentioned PartCool parameters, hence the term extension as "PartCool &Control”.
  • Virtually all changes in the Tribivari system as well as in the process as well as in the environment can be compensated by PartCool & Control, because thanks to the data stored in the CU for the respective work process (and "only” as an extra or interpolation of directly available data).
  • the respective corresponding compression behavior of the Tribivari system can be optimally adapted in each case.
  • the control unit of the Tribivari system according to the invention can now adjust the internal compression ratio of the current situation at any time ideal via the regulation of partial gas flows via additional Partauslass openings (15):
  • This regulating tool in operation is referred to as "n r adaptation" ,
  • ActionStep ReactionCheck is a constant self-learning and iterative method, which can be regarded both as a (self-) diagnostic tool and as a regulatory tool, because the system responses also draw conclusions about the current state of the Tribivari system discover.
  • the aforementioned regulating tools are not only to be used individually, but in particular also combined and evaluated.
  • PartCool & Control and Iii adaptation via the CU's own algorithm are always carried out in a coordinated manner, preferably evaluated and performed in combination by ActionStep ReactionCheck.
  • the filing of the results in the CU's own database constantly increases the knowledge of this Tribivari system and thus belongs to the Tribivari intelligence.
  • the evaluation of measures carried out is an essential prerequisite for the above-mentioned regulations.
  • a volume flow measurement for the pumped medium is generally too time-consuming, but would be a nice relief if it is carried out or is available.
  • the cooling fluid flows are application-specific for the particular situation according to the algorithm stored in the CU and flexibly based on current experience of the CU by the respective optimum is sought, in particular, the sufficient heat dissipation via a conventional external heat exchanger with advantageous temperature differences taken into account becomes.
  • the CU will forward its status in good time to higher-level service and maintenance points in order to permanently ensure the maintenance, care, maintenance and service as well as the availability of this system.
  • the Tribivari system is designed to be self-learning by continuously updating the analysis data for each CU under the respective process conditions and continuously optimizing them further using ActionStep ReactionCheck and storing them in the CU's own database.
  • Compressor individually per machine detects e.g. by "inversing" or
  • Align working space component such that on the one hand crash (ie gap consumption) safe (depending on the size of the machine, for example, with about 15%
  • the CU is always familiar with the condition of the compressor due to the control of the heat balance and the thermal expansion behavior of the workspace components stored in the CU.
  • working space space between inlet (1 1) and outlet (12)
  • the working space is determined by the pair of spindle rotors (2 and 3) and the surrounding compressor housing (1) with the narrow (in the range of 0.1 mm and smaller) gap values Axy of the respective components.
  • the desired compression of the pumped medium takes place via the working space components, ie spindle rotor pair (2 and 3) and compressor housing (1).
  • the CU as a control unit (25) monitors not only the screw compressor as described regulates and performs optimally, but the user with its complete system / factory control of the automation technology as industrial control in the so-called , "Process control technology” not only communicates (eg Profibus system) but also actively participates, for example, the load management for the entire (at least for this user) system, which consists of the individual compressor systems, each with its own CU (25), so is managed / regulated, so that, for example, expensive power peaks are avoided, which then belongs to the term "Industry-4.0".
  • Processe not only communicates (eg Profibus system) but also actively participates, for example, the load management for the entire (at least for this user) system, which consists of the individual compressor systems, each with its own CU (25), so is managed / regulated, so that, for example, expensive power peaks are avoided, which then belongs to the term "Industry-4.0".
  • a dot is simply set as the index instead of the subscript, so that e.g. R.F2 means RF2 and here denotes the root radius on the 2-toothed spindle rotor, where:
  • WK stands for pitch circle
  • the 3-tooth spindle rotor (3) 1 shows by way of example a 2-toothed spindle rotor (2) in longitudinal section with rotor geometry according to the invention and with cylindrical evaporator cooling bore (6) according to the invention and adapted displacement profile footing wall thicknesses w for the supporting foot base body (32) using the example of FIG -Rotors with detail to the steam outlet (14) over several (balanced with the necessary cross-section ⁇ ) transverse bores from the cylindrical evaporator cooling bore (6) with the radii values, which are carried out as follows: for the preferably blowhole-free profile pairing the gas delivery "external thread" (31) on the 2-toothed spindle rotor above the pitch circle line (37).
  • the drive motor (18) consists of a motor rotor (rotatably on the carrier shaft 4) and a motor stator package with the stator electrical windings (in vertical cross-hatching),
  • Extraction to the vacuum pump (29) starts at the neutral chambers (13) of the working area shaft bushings, in order to protect the bearings from the pumped medium if necessary
  • Fig. 2 shows an example of a cooling circuit with diversion of t 0 cooling fluid (9) from the circuit with cooling fluid injection (33) in the compressor working space per operating point targeted adjustment of the internal compressor volume ratio as iV value by additional partial outlet -Openings (15), with steam outlet (14) per workspace component, ie housing (1) and rotor pair (2 and 3), in the inlet space (1 1) shown
  • the expansion valve which is still shown, is preferably replaced with water vapor as the circulation medium via the simple height difference with the use of gravity as the so-called hydrostatic pressure difference (the present illustration relating to the direction of gravity would then have to be adapted).
  • the control unit (25) receives and processes various signals to the current operating requirements, to the entire circulation system and esp. Also from the compressor according to the invention in particular via the Regulierorgane (38) to adjust the compressor components for each operating point such that the requirements are met in the best possible way - only with the Control Unit (25) can the system work reliably and efficiently (in practice a "New Intelligence").
  • FIG. 3 shows, by way of example, a pair of spindle rotors with an adaptation of the [(z) - Nerte in the rotor longitudinal axis direction simplified as a projection in a common plane, because the rotor axes of rotation are at the angle alpha to each other and would have to be represented three-dimensionally, for the different according to positions E, S, V and L according to FIG. 5
  • this design achieves significantly more head area and thus an increased pumping speed relative to the cross-section, which is the aim of water vapor compression.
  • the 2-toothed spindle rotor also has the larger cooling bore for heat dissipation during compaction, so that the component heat balance with regard to heat absorption and heat dissipation is improved.
  • the 2z rotor has a 1.5 times higher rotational speed than the 3z rotor and accordingly it is embodied according to the invention in such a way that this 2-toothed spindle rotor achieves the more rigid shaft thanks to RF2> RF3 at reduced (by means of YF2> 90 °) mass has, which has a favorable effect with respect.
  • RF2> RF3 at reduced (by means of YF2> 90 °) mass has, which has a favorable effect with respect.
  • Increasing the critical bending speed, because the 2-toothed spindle rotor yes yes must also rotate faster and accordingly with the higher bending critical speed limit is carried out according to the invention.
  • the slower 3z rotor has a lower bending critical speed due to the lower bending stiffness, but it also rotates slower.
  • the rotor pair is now designed in such a way that the critical bending speed at the 2z rotor is 1.5 times higher than the critical bending speed at the 3z rotor.
  • FIG. 5 shows by way of example: rotors of FIG. 1 and FIG. 3 paired
  • FIG. 6 shows by way of example a total of 4 CAD representations for:
  • each spindle rotor with carrier shaft, bearing, drive motor and measuring system as a completely assembled and balanced unit (40), ready for mounting and henceforth unchanged, shown here only with the example of the 2-toothed spindle rotor, dto. for the 3-toothed spindle rotor, where the cylindrical. Flattening (27) at the 2z rotor input is not yet shown.
  • Both rotary units mounted in the pot housing plus frequency converter (22 and 23) per motor incl.
  • FU control unit (24) which communicates with the control unit (25) for continuous data exchange, which in turn is connected to the process control of the user is.
  • the motor windings of the two drive motors (18 and 19) are protected, for example, by vacuum-proof potting the motor stator winding packages or by retracted gap between the motor stator and motor rotor, etc.
  • FIG. 8 shows, by way of example, an illustration of the compression process in the pressure-enthalpy diagram in the case of water vapor compression, showing the improvement due to the intensive evaporator heat removal during compression
  • cylindrical evaporator cooling bore (6) is designed in a multiple cylindrically stepped form, as a kind of "terraces" with the overflow edge as shown by way of example in FIG.
  • cooling fluid When cooling fluid is generally referred to here, it means the R718 known in refrigeration, which is naturally compressed at the chosen negative pressure as water vapor in the positive displacement machine according to the invention, or in liquid form as cooling fluid (9) for cooling the components by evaporation ,
  • the combination with the refrigerant R744 as CO2 is advantageous (as a 2-stage solution, also known as "cascade").
  • the invention relates to the water vapor compression for the refrigeration, air conditioning and heat pump technology, both for right-handed and left-handed (Carnot) cycles.
  • a dry 2-shaft displacement machine is proposed as a spindle compressor according to the invention, the spindle rotors (2 and 3) have a rotor pair center distance, on the inlet side (1 1) at least 10% larger than on the exhaust side (12), driven by electronic motor pair (18 + 19) spindle rotor (2 + 3) synchronization and each spindle rotor is provided with an internal cooling, the crossing angle alpha between the two rotor axes of rotation in combination with the respective (z) value in RotorlFigsachsutter is carried out such that per spindle rotor a preferably cylindrical evaporator cooling bore (6) with minimal wall thickness w on supporting comfortably ground emotions (32) arises while taking into account the (preferably) blowhole-free profile design the gas delivery external thread (31) and "spindle rotor specific
  • spindle rotor preferably with 2-toothed gas supply external thread (31), short "2z rotor” called, preferably made of an aluminum alloy with good thermal conductivity (preferably above 150 W / m / K), rotationally fixed on supporting points (7 ) on a steel shaft (4) and inside a cylindrical evaporator cooling bore (6) with radius Rc2 having
  • spindle rotor preferably with 3-toothed gas supply external thread (31), short "3z rotor” called, preferably made of an aluminum alloy with good thermal conductivity (preferably above 150 W / m / K), rotationally fixed on supporting points (7 ) on a steel shaft (5) and inside a cylindrical evaporator cooling bore (6) with radius Rc3 having
  • 3z rotor carrier shaft with the 3z rotor rotatably connected to radius Rw3 (preferably pressed) with central cooling fluid supply hole (5.a), preferably in one piece at the same time also shaft for the 3z drive motor (19)
  • Cooling fluid flow for cooling the compressor working chamber components, ie rotor pair and housing either branched off from the circulation medium (34) according to the example in FIG. 2 or as a separate cooling fluid flow according to FIG. 6d in general, where for example:
  • Cooling fluid flow to the compressor housing for larger rotor lengths (eg> 500 mm) can be divided into: 9.1 a Cooling fluid flow through a section of the compressor housing (eg housing outlet side) 9.1 b Cooling fluid flow through another section of the compressor housing (eg central area) Cooling fluid flow to the 2z rotor
  • Cooling fluid guide grooves with the respective radius Rc per cylindrical evaporator cooling bore (6) with groove base surfaces at an angle of inclination ⁇ , which is preferably 170 ° ⁇ 180 °, and the cooling fluid guide grooves as a thread with the largest possible pitch as in ( 31)
  • Cooling fluid distributor overflow grooves (with undersized cross-section) vzw. in the groove bottom of (16)
  • 2z drive motor as a direct drive for the 2z rotor, vzw. designed as a synchronous motor
  • 3z drive motor as a direct drive for the 3z rotor, vzw. designed as a synchronous motor
  • FU-Control-Unit designated as "FU-CU"
  • FU-CU for both frequency inverters FU.2 (22) and FU.3 (23), where the FU-CU directly exchanges the operating data with the control unit (25).
  • Control unit CU as a control and regulation unit with evaluation of the respective current measured values and based output of the control signals for intelligent operation of the spindle compressor in preferably stored in CU memory links and data as well as learning interdependencies between each incoming measured values and the gap values according to previous simulation, verification and ongoing experience, the control unit is connected to FU-CU (24) as well as the user side with the process control technology for its application system as well as factory control iS of "Industry 4.0" Spacer / spacer discs, preferably as so-called.
  • “Slicing discs” designed for individual fixing of the respective spindle rotor in the rotor longitudinal axis direction for targeted gap value adjustment as A2.1 value on the 2z rotor (2) or as A3.1 value on the 3z rotor (3) cylindrical flattening (as 2) over the radius RKE2 at its rotor inlet side circulation medium through the evaporator (35) for heat absorption (as a core task in refrigeration ) Vacuum pump to remove foreign gases and to generate the necessary negative pressure for the steam cycle, preferably in the neutral spaces (13) sucking to protect the (rotor) bearings.
  • WK Pitch circle line
  • Vibration sensors to detect altered residual imbalance suggestions by different amounts of cooling fluid per spindle rotor internal cooling unit rotation per spindle rotor system , each fully assembled and balanced, primarily consisting of:
  • a total of two pieces of rotary units (40) per spindle compressor vzw. is preferably PAGE INTENTIONALLY LEFT BLANK

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un compresseur à vis réalisé sous la forme d'une machine volumétrique rotative à deux arbres fonctionnant sans fluide de travail dans un espace de travail pour le refoulement et la compression d'un fluide d'alimentation gazeux, de préférence de la vapeur d'eau. Le compresseur est muni d'une paire de rotors hélicoïdaux dans un carter de compresseur (1) qui présente un espace de collecte d'entrée (11) et un espace de collecte de sortie (12). La distance entre les axes de la paire de rotors hélicoïdaux est d'au moins 10 % plus grande à l'extrémité côté entrée qu'à l'extrémité côté sortie. Chacun des deux rotors hélicoïdaux (2, 3) est entraîné par un moteur électrique (18, 19), et les moteurs électriques (18, 19) sont commandés par synchronisation électronique, de sorte que les rotors hélicoïdaux (2, 3) tournent sans contact.
PCT/EP2018/051005 2017-01-17 2018-01-16 Compresseur de vapeur d'eau comportant une machine volumétrique de compression à sec en tant que compresseur à vis WO2018134200A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP18701293.5A EP3571408A1 (fr) 2017-01-17 2018-01-16 Compresseur de vapeur d'eau comportant une machine volumétrique de compression à sec en tant que compresseur à vis
US16/478,216 US20200386228A1 (en) 2017-01-17 2018-01-16 Steam compressor comprising a dry positive-displacement unit as a spindle compressor
JP2019538431A JP2020505544A (ja) 2017-01-17 2018-01-16 スピンドル圧縮機として機能する乾式容積型装置を含む蒸気圧縮機
CN201880018982.3A CN110520626A (zh) 2017-01-17 2018-01-16 作为主轴压缩机的包括干式正位移单元的蒸汽压缩机

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DEDE102017000382.3 2017-01-17
DEDE102017000381.5 2017-01-17
DE102017000381.5A DE102017000381A1 (de) 2017-01-17 2017-01-17 Trockene Wasserdampf-Verdrängermaschine
DE102017000382.3A DE102017000382A1 (de) 2017-01-17 2017-01-17 Wasserdampf-Verdichtung mit intelligentem Trockenläufer-Verdränger

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020200491A1 (fr) * 2019-03-31 2020-10-08 Steffen Klein Agent réfrigérant à base d'eau pour une machine de travail thermique et machine de travail thermique pourvue d'un tel agent réfrigérant

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Publication number Priority date Publication date Assignee Title
WO2013167605A2 (fr) * 2012-05-08 2013-11-14 Ralf Steffens Compresseur à vis
DE102013009040A1 (de) 2013-05-28 2014-12-04 Ralf Steffens Spindelkompressor mit hoher innerer Verdichtung
DE102015108790A1 (de) 2014-06-03 2015-12-03 Ralf Steffens Lagerung für einen Spindelkompressor mit hoher innerer Verdichtung

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DE19749572A1 (de) * 1997-11-10 1999-05-12 Peter Dipl Ing Frieden Trockenlaufender Schraubenverdichter oder Vakuumpumpe
DE19839501A1 (de) * 1998-08-29 2000-03-02 Leybold Vakuum Gmbh Trockenverdichtende Schraubenspindelpumpe
CN201013589Y (zh) * 2006-12-31 2008-01-30 西安交通大学 锥型双螺杆压缩机驱动机构

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013167605A2 (fr) * 2012-05-08 2013-11-14 Ralf Steffens Compresseur à vis
DE102013009040A1 (de) 2013-05-28 2014-12-04 Ralf Steffens Spindelkompressor mit hoher innerer Verdichtung
DE102015108790A1 (de) 2014-06-03 2015-12-03 Ralf Steffens Lagerung für einen Spindelkompressor mit hoher innerer Verdichtung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020200491A1 (fr) * 2019-03-31 2020-10-08 Steffen Klein Agent réfrigérant à base d'eau pour une machine de travail thermique et machine de travail thermique pourvue d'un tel agent réfrigérant

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US20200386228A1 (en) 2020-12-10
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