US20200386228A1 - Steam compressor comprising a dry positive-displacement unit as a spindle compressor - Google Patents

Steam compressor comprising a dry positive-displacement unit as a spindle compressor Download PDF

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US20200386228A1
US20200386228A1 US16/478,216 US201816478216A US2020386228A1 US 20200386228 A1 US20200386228 A1 US 20200386228A1 US 201816478216 A US201816478216 A US 201816478216A US 2020386228 A1 US2020386228 A1 US 2020386228A1
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Prior art keywords
spindle
rotor
cooling fluid
cooling
compressor
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US16/478,216
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English (en)
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Ralf Steffens
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Individual
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Priority claimed from DE102017000381.5A external-priority patent/DE102017000381A1/de
Priority claimed from DE102017000382.3A external-priority patent/DE102017000382A1/de
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Publication of US20200386228A1 publication Critical patent/US20200386228A1/en
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    • 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
    • F04C18/12—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
    • F04C18/08—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
    • F04C18/48—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

  • Cyclic processes are preferably described on the basis of Carnot's theorem, with heat output and heat absorption as well as a compressor as drive for the circulation medium in the gaseous phase. Cyclic processes are used very frequently and have become indispensable in our daily lives. These processes include clockwise and anticlockwise Carnot processes, with desired/targeted heat absorption to fulfil a cooling task (in the refrigeration and air conditioning field) or with desired/targeted heat output to fulfil a heating task (keyword “heat pump”) with heat exchangers for heat absorption and heat output.
  • a drive in the form of a compressor for the circulation medium in its gaseous phase is generally required.
  • the circulation medium and its specific properties is critical. There are various artificial circulation media (generally chemically produced, such as HFCs and HFOs) and natural circulation media (such as ammonia, propane, propylene, isobutane, ethane.
  • Water is irrefutably ideal as a circulation medium because of its general availability and the fact that it is completely non-toxic, can be safely used at low pressures in the form of steam, meets even the most stringent of guidelines and safety regulations, is resource-friendly, environmentally friendly, low maintenance, efficient and practically without any risk potential (incombustible, non-explosive, uncritical).
  • turbomachines allow only moderately satisfactory temperature and pressure conditions. If there were a more efficient compressor solution here, steam would be a significant advancement as a circulation medium because of its enormous advantages.
  • the object of the present invention is to provide the compression of (preferably) steam in the known working field and pressure range, which is generally referred to as a rough vacuum, by a positive-displacement machine which handles the desired pressure differences and the large p/p pressure conditions with the typically steep characteristic curve for a positive-displacement machine (i.e. pressure values over volume flow with the corresponding working points), wherein this machine must be completely dry running (no operating fluid) and should have a total efficacy for the entire system that is better for the entire field of application as compared to current turbo compressors, so that the user requirements in the field of refrigeration and in heat pumps as well as other (Carnot) cyclic processes are better met, especially in terms of a greater pressure range.
  • a positive-displacement machine which handles the desired pressure differences and the large p/p pressure conditions with the typically steep characteristic curve for a positive-displacement machine (i.e. pressure values over volume flow with the corresponding working points), wherein this machine must be completely dry running (no operating fluid) and should have
  • This object of compressing steam at pressures below atmospheric pressure preferably between 6 mbar and 300 mbar, i.e. in the classic rough vacuum region
  • This object of compressing steam at pressures below atmospheric pressure preferably between 6 mbar and 300 mbar, i.e. in the classic rough vacuum region
  • in a power range of less than 1 kW to well over 100 kW as refrigeration cycle power for refrigeration technology (i.e.
  • a compressor works in principle between the following two limits:
  • Tribivari Unlike the currently only “semi-mounted” (screws already worked beforehand) controllers, the intelligence of Tribivari is a conceptual part of this new compressor technology, since the entire operation is managed by the control unit individually (i.e. specifically to each Tribivari with its own tolerances and particular use conditions/deviations) under all conditions, including constant changes thereto, with independent self-diagnosis(! and prognosis with ongoing adaptation to the process under various conditions (colder/hotter environment, poorer cooling, etc.). This is the new Tribivari intelligence.
  • Tribivari is fundamentally superior here in that it fulfils 3 features simultaneously:
  • Tribivari Helps Itself by Fixing Itself Practically Single-Handedly, i.e.:
  • Tribivari is intelligent insofar as Tribivari with the mentioned (self-)diagnostic tools in the form of “self-diagnosis” firstly recognises, itself, if Tribivari changes due to wear, abrasion, dirtying and/or deposit formation, and can then adjust its operating behaviour on that basis via the described control tools, specifically this means that, for example at each operating point, as required by the user's process operating point in the particular situation,
  • the most appropriate gap values are set via PartCool or PartCool&Control, b) each optimal inner compression ratio is set via post-inlet and/or pre-outlet, c) and the most suitable rotor speed is set.
  • the current state (due to wear, abrasion and/or dirtying, deposit formation possibly changed) of Tribivari is taken into account in the algorithm of the control unit, as are also the current ambient conditions (hotter, colder, dirtied heat exchangers, etc.) and the currently desired operating requirements (i.e. in terms of volume flow, pressure level, but also allowable power consumption in the sense of avoiding expensive power peaks, etc.).
  • Tribivari uses its own (self-)diagnostic tools, i.e. by means of k 0 speed measurement and/or ⁇ measurement and/or algorithm-measured value comparison and/or ⁇ rotor pair check and/or inverse cooling, etc., incl. any (evaluation) combination of these tools, to determine that the gap values have decreased in the outlet area, for example by deposit formation/dirtying.
  • Tribivari can determine this via the algorithm in its own control unit, where individual guideline values (stored during the assembly of this Tribivari) are available for the different measured values and are stored with the respective links, relationships and interpretations, which are then compared with the incoming measured values.
  • Tribivari can not only be operated safely, but also in the optimum (in the sense of minimal energy requirement) range.
  • it can even be determined individually for each spindle rotor which gap value has decreased, namely ⁇ 21 or ⁇ 3.1, in order accordingly to increase the relevant cooling fluid flow 9 . 2 or 9 . 3 according to the value tables present in the CU (for example previously calculated by FEM simulations).
  • Tribivari determines via its own (self-)diagnostic tools that the gap values have increased in the inlet area, for example due to abrasion/wear, noticeable by way of poorer compression behaviour.
  • the cooling fluid flow 9 . 1 b at the compressor housing inlet area must be increased.
  • PartCool Based on “PartCool” as a self-diagnosis by means of:
  • the k 0 speed measurement is possibly also combined with ⁇ p measurement with the inverse cooling as an ongoing operational check for reliable crash avoidance by means of extrapolation.
  • the outlet (over)pressure achieved is measured at the closed outlet for different rotor speeds and, thanks to PartCool, at defined(!) thermal situations**°° of the relevant (i.e. in particular the working space) compressor components (and the resultant individual gap conditions), and the quotient of outlet-to-inlet pressure gives the desired k 0 speed value for this rotor speed, and thus as a value table or as a functional representation:
  • Inverse cooling stimulation of a “wrong” (inverse) component cooling with a component temperature difference, as no longer occurs later during operation (because constantly monitored by the CU in this sense as well)
  • Both the k 0 speed measurement and the inverse cooling are repeatedly used during operation to detect changes within the lifetime of this compressor.
  • the inverse cooling is also executable via an algorithm stored in the CU 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 by way of example:
  • PartCool also called “PartCool&Control”
  • PartCool&Control also called “PartCool&Control”
  • ⁇ i adaptation FU speed variation
  • Tribivari spindle compressors 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 these are 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 ), so that the “defined temperature conditions” described hereinafter for the entire Tribivari spindle compressor are always known sufficiently precisely in the CU ( 25 ) or can be converted via interpolations (known geometry and material properties) with the resultant individual gap conditions also widely known.
  • Separate cooling fluid temperature ranges at the reservoir ( 10 ) facilitate the achievement of defined temperature conditions by removing cooling fluid selectively for the relevant component.
  • At least one ⁇ T BT previously defined for this spindle compressor machine size should be established as the setpoint component temperature difference value and should ensure, via the simple (slow) rotatability monitoring, that there is no contact (touching) of the working space components.
  • the control unit ( 25 ) then knows how to adjust the particular cooling fluid flows of the working space components such that this ⁇ T BT value is not exceeded, and therefore the crash can always be reliably avoided.
  • This targeted regulation of the individual screw compressor components is also referred to below as “temperature control”.
  • the inverse cooling is additionally performed by ⁇ T BT value examination also linked with measures as described under “Combination & Evaluation”.
  • the ⁇ T BT values are thus considered to still be reliable, and component temperature differences checked multiple times by inverse cooling are continuously observed and preserved by the CU during operation in that the ⁇ T BT values in question are not exceeded.
  • the “PartCool” can then be adjusted in a regulated manner during later operation in such a way that the gap values in each area are optimal: Optimal means that on the one hand a crash (i.e. gap reduction) is safely avoided, which is now finally possible thanks to the knowledge of the respective ⁇ T BT values, and on the other hand the internal gap leakage can be monitored via the gap values managed by PartCool in accordance with the present simulation of the compressor process in such a way that the efficacy is maximised for precisely the current compression process.
  • the inverse cooling does not have to be driven until the first contact of the working space components as a check of the post-rotatability limit (also because of the risk of surface damage), in that the post-rotatability is ensured with a ⁇ T BT of the inverse cooling defined previously in the CU (i.e. a clearly defined temperature level of the working space components) on the one hand, and on the other hand in that a ⁇ p measurement and/or k 0 speed measurement are/is performed, wherein the values then determined by these methods are compared with the basic reference and comparison values that are appropriate for this inverse cooling and are stored in the CU.
  • Tribivari intelligence by way of example:
  • ES Electronic motor pair-spindle rotor synchronisation
  • ActionStep-ReactionCheck Improvements are noted when, at a working point at an existing pressure p B , the power requirement (which is even known at ES for each rotor) is reduced or minimal at a known speed, wherein the gap leakage and entropy balance are assessed in the algorithm of the CU via the temperature feedback ( 32 . e ) thanks to simulations and ongoing learning (writing of the “experiences” of this machine), so that the compr. efficacy can be specified. This is henceforth referred to as the objective of an efficient compression process for the current situation.
  • a volume flow measurement for the conveyed medium is generally too time-consuming, but would provide a nice facilitation if it were carried out or were available. Instead of improvements, of course, deteriorations in the compression behaviour also can be noted and are evaluated by the control unit, in order then to be able to initiate appropriate regulation measures (in particular by PartCool&Control etc.).
  • the cooling fluid flows are regulated by the CU in an application-specific manner for the particular situation in accordance with the algorithm stored in the CU and flexibly based on current experience by seeking the relevant optimum, wherein in particular the sufficient heat dissipation via a conventional external heat exchanger with advantageous temperature differences is taken into account.
  • the CU will forward its status in good time to higher-level service and maintenance positions in order to permanently ensure the upkeep, 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 individually for each CU under the particular process conditions and continuously optimising them further using ActionStep-ReactionCheck and storing them in the CU's own database.
  • working space space between inlet ( 11 ) and outlet ( 12 )
  • the working space is defined by the pair of spindle rotors ( 2 and 3 ) and the surrounding compressor housing ( 1 ) with the narrow (in the region of 0.1 mm and smaller) gap values Oxy of the various components.
  • the desired compression of the conveyed medium takes place via the working space components, i.e. spindle rotor pair ( 2 and 3 ) and compressor housing ( 1 ).
  • the CU as a control unit ( 25 ) not only monitors, regulates and optimally manages the spindle compressor as described, but at the user location also not only communicates (for example Profibus system) with the entire system/plant controller via automation technology as industrial controller in the “process management technology”, but also actively participates therein, for example by managing/regulating the load management for the entire (at least in the case of this user) system, consisting of the individual compressor systems with their own CU ( 25 ) in each case, and therefore for example costly current peaks are avoided, wherein this then belongs to the term “Industry-4.0”.
  • This also includes (preferably) at the same time (if the user agrees) also feedback to the supplier (or to the suppliers if there are more than one) regarding the current state of the compressor system with all individual systems including prognosis for further conduct with appropriate maintenance recommendation regarding the known diagnostic systems (for example vibration sensors, temperature profiles, etc.) with the corresponding evaluations (software).
  • known diagnostic systems for example vibration sensors, temperature profiles, etc.
  • this also includes the constant and continuous adaptation to changed or changing process conditions, for example by deposit formation, dirtying, wear, etc., but also by external environmental conditions such as temperature level (for example warmer or colder environment), another desired pressure level, whereupon the intelligent CU system ( 25 ) responds by appropriate adjustment of the cooling water amounts, equalisation of the inner compression rate by means of additional partial outlet openings ( 15 ) etc., as well as all measures for self-diagnosis to determine the current state of this compressor in this application and prognosis over the further course with appropriate remedial action ranging from adjustment of the cooling fluid amounts up to a warning to the operator.
  • temperature level for example warmer or colder environment
  • additional partial outlet openings ( 15 ) etc. as well as all measures for self-diagnosis to determine the current state of this compressor in this application and prognosis over the further course with appropriate remedial action ranging from adjustment of the cooling fluid amounts up to a warning to the operator.
  • R.F2 means R F2 and thus here denotes the root radius on the 2-toothed spindle rotor, wherein:
  • FIG. 1 shows, by way of example, a 2-toothed spindle rotor ( 2 ) in longitudinal section with rotor geometry according to the invention and with cylindrical evaporator cooling bore ( 6 ) according to the invention and adapted positive-displacement profile root-base wall thickness w for the load-bearing root-base body ( 32 ) on the basis of the example of the 2t rotor with detail of the steam outlet ( 14 ) over a plurality of (balanced with the necessary cross-section ⁇ ) transverse bores from the cylindrical evaporator cooling bore ( 6 ) with the radii values which are as follows:
  • the gas-conveying “external thread” ( 31 ) on the 2-toothed spindle rotor is located above the pitch circle line ( 37 ).
  • the drive motor ( 18 ) consists of a motor rotor (mounted on the carrier shaft 4 for conjoint rotation) and a motor stator assembly with the electrical stator motor windings (shown by squared hatching), optional: extraction to the vacuum pump ( 29 ) starts at the neutral chambers ( 13 ) of the working space shaft bushings, in order to protect the bearings from the conveyed medium as necessary
  • FIG. 2 shows, by way of example, a cooling circuit with diversion of to cooling fluid ( 9 ) from the circuit, with cooling fluid injection ( 33 ) into the compressor working space per working point, targeted adjustment of the inner compressor volume ratio as iV value by additional partial outlet openings ( 15 ), with steam outlet ( 14 ) per working space component, i.e. housing ( 1 ) and rotor pair ( 2 and 3 ), shown in the inlet space ( 11 )
  • the expansion valve which is also shown, in the case of steam as the circulation medium, is preferably replaced via the simple height difference with the use of gravity as a “hydrostatic pressure difference” (the present illustration would then have to be adapted to the direction of the force of gravity).
  • the control unit ( 25 ) receives and processes various signals regarding the current operating requirements, the entire circulation system and in particular also from the compressor according to the invention, in order in particular to adjust the compressor components for each working point via the regulation members ( 38 ), such that the requirements are met in the best possible 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 spindle rotor pair end-face section with an adaptation of the ⁇ (z) values in the rotor longitudinal axis direction simplified as a projection in a common plane, because the rotor axes of rotation are at the angle alpha to each other and ought to be shown three-dimensionally, for the various positions E, S, V and L of FIG. 5
  • FIG. 5 shows by way of example: rotors from FIG. 1 and FIG. 3 paired to show the overall rotor geometry and indicating the crossing angle alpha and the spindle rotor pairing with the engagement lens area engaging centrally with one another
  • FIG. 6 shows, by way of example, a total of 4 CAD illustrations, showing:
  • FIG. 6 shows:
  • FIG. 8 shows, by way of example, an illustration of the compression process in a pressure-enthalpy graph in the case of steam compression, showing the improvement due to the intensive evaporator heat dissipation during compression
  • HydroCom Prior art represented by turbo, which must work in two stages with intermediate cooling, as compared to the improvement of the invention, here referred to as “HydroCom” (abbreviated to HC)
  • FIG. 9 shows, by way of example: an Excel design table with example values for the parameter values for the positions E, S, V and L, stated by way of example, in the rotor longitudinal axis direction for the spindle rotor pair with individual values per spindle rotor, the indicated power specifications being only quite rough and constituting provisional reference values.
  • an Excel design table with example values for the parameter values for the positions E, S, V and L, stated by way of example, in the rotor longitudinal axis direction for the spindle rotor pair with individual values per spindle rotor, the indicated power specifications being only quite rough and constituting provisional reference values.
  • both the selection of the named positions and the selection of other parameter values for the particular application-specific requirement profile are imperative.
  • cylindrical evaporator cooling bore ( 6 ) is designed in a multi-stepped cylindrical form, as “terraces” so to speak, with the overflow edge as shown by way of example in FIG. 1 .
  • cooling fluid what is meant here is the R718 cooling fluid known from the field of refrigeration, which is naturally compressed at the chosen negative pressure as steam in the positive-displacement machine according to the invention, or in liquid form as cooling fluid ( 9 ) for component cooling by evaporation.
  • the combination with the refrigerant R744 as CO 2 (as a 2-stage solution, also known as a “cascade”) is advantageous for lower temperature values (for example for deep freezing).
  • the invention relates to steam compression for refrigeration, air conditioning and heat pump technology, both for clockwise and anticlockwise (Carnot) cyclic processes.
  • a dry 2-shaft positive-displacement machine as spindle compressor, the spindle rotors ( 2 and 3 ) of which have a rotor pair centre distance which on the inlet side ( 11 ) is at least 10% greater than on the outlet side ( 12 ), and being driven by electronic motor pair ( 18 + 19 )-spindle rotor ( 2 + 3 ) synchronisation, and each spindle rotor being provided with internal cooling, wherein the crossing angle alpha between the two rotor axes of rotation is formed in combination with the corresponding ⁇ (z) value in the rotor longitudinal axis direction in such a way that a preferably cylindrical evaporator cooling bore ( 6 ) with minimal wall thickness w at the supporting root-base body ( 32 ) is formed

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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)
US16/478,216 2017-01-17 2018-01-16 Steam compressor comprising a dry positive-displacement unit as a spindle compressor Abandoned US20200386228A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE102017000381.5 2017-01-17
DE102017000381.5A DE102017000381A1 (de) 2017-01-17 2017-01-17 Trockene Wasserdampf-Verdrängermaschine
DE102017000382.3 2017-01-17
DE102017000382.3A DE102017000382A1 (de) 2017-01-17 2017-01-17 Wasserdampf-Verdichtung mit intelligentem Trockenläufer-Verdränger
PCT/EP2018/051005 WO2018134200A1 (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

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US20200386228A1 true US20200386228A1 (en) 2020-12-10

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US16/478,216 Abandoned US20200386228A1 (en) 2017-01-17 2018-01-16 Steam compressor comprising a dry positive-displacement unit as a spindle compressor

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US (1) US20200386228A1 (fr)
EP (1) EP3571408A1 (fr)
JP (1) JP2020505544A (fr)
CN (1) CN110520626A (fr)
WO (1) WO2018134200A1 (fr)

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DE102019002297A1 (de) 2019-03-31 2020-10-01 Steffen Klein Erweiterung des R718-Einsatzbereichs

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE102012009103A1 (de) * 2012-05-08 2013-11-14 Ralf Steffens Spindelverdichter
DE102013009040B4 (de) * 2013-05-28 2024-04-11 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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CN110520626A (zh) 2019-11-29
JP2020505544A (ja) 2020-02-20
WO2018134200A1 (fr) 2018-07-26

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