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    • 专利摘要:
    Cellular motor according to the basic principle of a multi-disc compressor with an eccentric to the housing (9) mounted rotor (4) with movable cell walls (5), which by rollers and a milled in both side walls (14) groove (8) counteracted positively to the centrifugal force, thereby results a non-contact run to the housing (9), the gap losses are minimized by a labyrinth seal at the end of the cell wall (5) and the working gas is supplied at a tuned angle, so that when fully expanded in the expanding cells ambient pressure, wherein the Design is in principle also suitable for an isothermal-like expansion by supplying fuel in the region of the expansion section and thus very favorable efficiencies are achieved, this also applies to the possible use as a compressor.
    公开号:AT514998A1
    申请号:T803/2013
    申请日:2013-10-18
    公开日:2015-05-15
    发明作者:Walter Ing Falkinger
    申请人:Walter Ing Falkinger；
    IPC主号:
    专利说明:

    Patent description cell wheel motor
    The subject cellular motor is based on the principle of a multi-plate compressor, where an eccentrically mounted and slotted rotor is provided with movable blades of steel or plastic, which are pressed by the centrifugal force to the housing and thus lead to dense cells. By the rotation arise expanding and decreasing cell volumes, where the suction and the compression of the gas take place. The contact forces of the lamellae by the centrifugal force to the housing wall cause friction, whereby the application limits in terms of speed and temperature are limited. The use for the purpose of compression is well known The use of the part of safely expanding cell volume for the expansion of a gas for utility power generation is not known in the literature because the usual temperature level of higher 500 to 600 ° C for contacting surfaces of the cell walls with the housing wall Use for such a purpose would not be technically permissible for several reasons.
    The invention is therefore based on the object to describe a construction in which the disadvantage of contacting surfaces of the cell wall and housing is made possible here non-contact run and working gas temperatures even above 1000 ° C for achieving a high thermodynamic efficiency is allowed. One aspect to be noted is that relatively simple means allow isothermal expansion by supplying fuel through the housing area at multiple points of expansion through holes through the housing wall, thus maintaining the working gas (air) at a high temperature level (technically equivalent to several Intermediate heaters) and expanded under power with improved efficiency.
    The invention achieves this object in that here a design is used in principle according to a slat compressor with the essential difference that the cell walls run without contact and the housing is protected from excessive temperatures and the heat expansions can be shaped by the choice of temperature and material. The construction consists of a shaft with multiple grooves for feather keys (1), which is mounted on the side for driving a generator, on the other end of a working machine (compressor) in a fixed bearing (2) and the opposite side in a movable bearing (3). Fixed to the shaft is the rotor (4), which is provided with a number of grooves in which the cell walls (5) are able to radially retract and extend the radial movement. The cell walls are provided with cooled pins for displacement (6) to guide the positively guided radial movement over rollers with a needle bearing (7) which are guided in an externally grease-lubricated groove (8). The shaft axis is arranged eccentrically to the housing axis. The housing (9) is equipped with 2 flanges (10) and the cooling jacket (11), in this space is the cooling medium (12), thermal oil or relaxed working gas at a temperature of about 350 ° C. The housing can in the region of expansion with a plurality of welded-on ribs or grooved grooves (13) for a good heat transfer to the expanded working gas and to increase the dimensional stability.
    The bearings for the shaft are integrated in the two side walls with cooling jacket (14), wosich also two grooves for labyrinth seals (15) and especially the groove (8) are provided for the guidance of the cell walls. In the housing cover for the seal (16) either a pack with a grease distribution ring (17) is provided or a mechanical seal. A bore (18) is supplied to the cooling air for the bolts for the cell walls. The cooling air supply for the rotor takes place in crossflow through the bore (19) and via bore (20) on the opposite side again discharged. The supply of cooling air takes place only over the upper half of the housing, since here are the elements to be cooled as the cell walls, whereas in the lower part, the cell walls is in the extended state and the space is empty and the air would go the least resistance with questionable cooling effect , The cell walls are supported radially by rolling elements (21), which are located in a cage (22) which is functionally assigned to a roller bearing. The sealing strips with labyrinth seals (23) have the task of minimizing the escape of working gas from the cells to the rotor slots. These strips are provided with cover plates (24), which also cover the insulation (25) against the rotor. The entry of the working gas via the pipe with two shafts (26) in order to achieve the fastest possible and complete filling by short paths. When using the expanded working gas as the cooling medium, the outlet takes place via the outlet pipe (27). When thermal oil is used as the cooling medium, the expanded working gas is expelled through also 2 wells over about half the circumference of that side of the narrowing cell volume. The cooling jacket, irrespective of the cooling medium, is provided with an insulation (28). The side walls are fixed to the base plate (29), displaceable on the non-locating side by the housing thermal expansions.
    It should be noted the following fact: Due to the eccentric bearing of housing and rotor shaft and thus the cell walls results in a different gap of the ends of the cell walls to the housing. For small units this is easily remedied by providing a labyrinth seal that is somewhat flattened, or radiused, and whose width is the cell wall. For larger units, minimizing the gap caused by a complex combination of angulation functions varying circumferentially in conjunction with the size of the eccentricity and the cell wall thickness is accountable and this difference is accounted for by the design of the groove, thus providing a constant minimized gap. The shape of the groove is not just a circle, but a slightly different curve shape, which can be traced with CNC milling machine exact.
    The rotational movement results in narrowing and expanding cross-sections where, when used as a motor, the working gas is supplied through a tuned angle of rotation in the area of expanding cell volumes, with further rotation the expansion occurs in widening cross-sections and the torque is generated by the differential pressures on the cell wheel walls. The position of the leading edge should be set so that there is a closed volume at the beginning, which at the end of the expansion is 1 bar abs. in general, in the ratio of the spec. Volumes of entry volume to exit volume of the respective cell. After complete expansion to 1 bar a. For example, the expanded working gas is exhausted in the open section where it is first used as the cooling air for the housing and, subsequently, as the combustion air, or through a recuperator, the heat release is also given to the incoming pressurized combustion air under combustion under pressure.
    Essentially, only the friction of the bearings for the cell walls in the groove in the sidewalls and the rolling elements in the slots of the rotor caused by the flexing force and / or the tangential and bending force components of the movable cell walls, as well as the rotor bearing, becomes effective as a loss. I would like to mention that here a force (power) is required to move the cell walls against the centrifugal force inwards.
    Over one half results in a Tangentialkomponente m Drehnchtung, in the other the same amount opposite and thereby cancel. Combined with the use of the exit air cooling from the housing, this results in a good thermodynamic expansion machine because by providing only roller friction this would be in a range of about 2 to 3% (apart from the thermodynamic losses by cooling the rotor and cell walls, this from the temperature level for a possible one Reintegration) with the benefit of a rotating motion. As efficiency at a working gas temperature of about 850 ° C and a system pressure of 7 bar a can be achieved about 40 to 50%, be given at a working gas temperature of about 1200 ° C by internal combustion about 50 to 60%, about the same as a Isothermal process at about 800 ° C, but where the performance compared to a polytropic expansion of 1200 ° C with the same size fails.
    A certain disadvantage is that there are different thermal expansions in the housing and the rotor or the cell walls, so that if the gap losses are minimized, the housing should be cooled to about 300 to 400 ° C (expanded working gas or thermal oil) and this results in some heat loss, which could be used in thermal oil for steam production and recycled to the working gas. However, when using working gas, substantially all of the heat in the form of elevated temperature is available to the combustion air or recuperator, thereby minimizing thermal losses. One way to reduce heat losses and yet achieve high working gas temperatures is to build the housing in layers. Inside a jacket made of heat-resistant steel, then an insulating layer of refractory material and the outside of the coat of normal steel, which absorbs the forces of pressure and thermal expansion. There are also usually different materials of rotor (normal steel) and for the cell walls (heat resistant steel) where the coefficients of thermal expansion (1.2 for normal steel, 1.8 mm / 100 ° Cm for heat resistant steel) and also the temperatures are very different, so a heating of the motor or the cell walls and the housing is required without load, so that the temperature-related columns considered close especially at the cell walls to the housing radially and axially and the power operation can take place. Since the resulting temperatures and thus the thermal expansions of the cell walls in operation can only be determined sufficiently at least in the initial design, a certain gap can be provided in advance, but the final cut can be applied in operation by a cutting edge made of hard metal in the region of the side wall of the extended cell walls scraping away any existing excess length due to thermal expansion and so there is a precisely defined small gap in the axial direction.
    The cell walls are designed to be cooled in the form of an air cross-flow in the rotomotors, introduced via a bore in the upper half, which is divided by sheets in the gap between the rotor and side wall and on the opposite side, the heated air is discharged, separated from the cooling air for the bolts of the Cell walls, which are supplied via grooves in the rotor and 2 holes in the cell wall to the bolts to ensure the cooling and a lubricating film at the needle bearings. The heat loss across the housing, as with almost any thermodynamic engine, depends on the one hand on the difference in temperature of wall and working gas and on the ratio of surface area of individual cells to cell volume, where larger units have a distinct advantage. With a layer construction of the housing wall, it is quite possible that the inner housing with a temperature of about 600 ° C. or higher (resistance of heat-resistant steel without strength resistance up to about 1100 ° C.) is kept approximately in the range mentioned, it is then important to what temperature the outer jacket has, and thus the expansion gaps in the interior, because the inner heat-resistant steel layer is somewhat constricted by the supporting outer jacket and can not stretch with the higher coefficient of thermal expansion over normal steel. The engine is in the opposite direction of rotation or arrangement of inlet and outlet mirror image also used as a compressor, where in terms of length, the ratio of the spec. Volumes of intake air and exit gas after the engine is to be used. It could also be otherwise used a generator with 2 stub shafts, where in each case one of the engine and the other hangs the compressor.
    Regarding process control, both the one given in the patent AT 501 504 B 1 2009-05-15 can be used with the working gas air with the heat input indirectly via a high-temperature heat exchanger and briefly mentioned here for repetition: isothermal-like compression by water injection in intake air,
    Preheating the working gas in a low-temperature heat exchanger, heat in a high-temperature heat exchanger, expansion in the engine, using the expanded gas as housing cooling air and then as combustion air for the wood chips, where after leaving the engine or the housing to be cooled, this is used as combustion air, but also in the direction in that a gas turbine process with recuperator is used here. From the principle of the motor, I would like to point out that this appears to be suitable for an isothermal-like expansion, with the highest efficiencies, if here at the housing periphery during the expansion in several places a gaseous fuel would be supplied, but also wood dust, which has a grain size that this over in the time interval burns the region of expansion or as the gas-fuel is supplied in several places. Since the gas is not subject to any particular requirements, gas which has been largely purified from ash can also be used from autothermal wood gasification under pressure (for example entrained flow gasification), with the advantage that the gas does not have to be cooled as usual in reciprocating piston engines (cold gas efficiency at approx 80%), but can be supplied to the engine uncooled, this brings at least compared to the reciprocating engine by about 10 to 15% better thermal yield from the wood or the entire system. It is at least a heat supply with multiple Zwischenerhitzungen the working gas air or flue gas with high excess air without much effort possible. The determination of the pressure for the compression and expansion is possible by shifting the inlet and outlet edge.
    Designations in Drawings FIG. 1 and FIG. 2 1 Rotor shaft with feather keys 16 Housing cover for sealing 2 Fixed bearing 17 Grease ring 3 Floating bearing 18 Bore Cooling air Bolt 4 Rotor 19 Bore Cooling air Crossflow 5 Movable cell walls 20 Bore Cooling air discharge 6 Cooled bolt 21 Rolling element for cell walls 7 Roller with needle bearing 22 Roller cage 8 Groove for positive guidance 23 Sealing strips with labyrinth seal 9 Housing 24 Covering plate for insulation 10 Flange 25 Insulation 11 Cooling jacket 26 Manholes Working gas inlet 12 Cooling medium 27 Outlet relaxed working gas 13 Ribs for surface enlargement 28 Insulation for cooling jacket 14 Side wall with cooling jacket 29 Base plate 15 grooves for labyrinth seals Proximity wise calculation of efficiency:
    Output data: Stationary plant operated with wood chippings, rotor diameter 540 mm, rotor length 500 mm, housing diameter 600 mm, eccentricity 30 mm, preheating by NT heat exchanger to approx. 400 ° C, in high temperature heat exchanger up to approx. 850 ° C, speed 750 to 1000 U / 80 kW (750 rpm), expansion stage up to approx. 110 kW (approx. 1000 rpm), compaction pressure 7 bar abs., wood chips supply approx. 3.5% of total air mass flow, water supply for isothermal - like compression approx 5%,
    I would like you to remember that the parameters chosen here are taken from, for example, where there are a number of different combinations of pressure and temperature that naturally lead to a different result a range of about 400 ° C with an inlet temperature of about 850 ° C where for the low temperature WT mainly mild steel can be used, which has a favorable effect on the cost. The stated values for the heat input via the specific heat capacity at constant pressure (cpml2) can basically be equated to the volume change work and the equal pressure part or the technical work on the expansion (qzul2 = wl2), where the theoretical efficiency can be determined by considering the compression work. Usually, suction air temperature calculated at 0 ° C, here 20 ° C to better match the situation. For the isothermal-like compression with a water injection, a temperature rise is required so as not to fall below the saturation limit and is at 7 bar abs. at about 85 ° C. The most important factors for the efficiency are the selected system pressure and the working gas temperature at the engine inlet and of course the process control.
    The isentropic efficiency for expansion as well as the heat losses during expansion and latency across the labyrinth seals was assumed to be 0.92. The need for wood with approximately 3.5% mass feed was calculated from the heating demand of the gas and also at the bucket wheel motor for work recovery be available. The supply of water vapor from the compression takes place with some energy expenditure, since here the water evaporates over the piston path and this mass must be compressed under expenditure of effort (on the way considered about 0.5 of the injected mass). The values used in the calculation for the mean spec. Heat capacity stems from tables of relevant literature.
    Moisture entry: approx. 5% water supply by injecting water into intake air. In addition, however, about 1.5% water intake by water evaporation due to differential temperature at the recuperator, as well as the additional mass feed for combustion, could not yet be considered fully protected, possibly only a total of 6.5% moisture input 5%.
    Isothermal compression up to 7 bar abs: W = R x T x ln pl / p 2 = 0.2872 kJ / kg.K x 293 K x ln 1/7 = -163.7 kJ / kg (t = 20 ° C) 0 , 2872 kJ / kg.K x 353 K x ln 1/7 = - 197.2 kJ / kg (t = 85 ° C)
    Arithmetic mean: -180.5 kJ / kg (- = energy to be supplied)
    Compression water vapor: in the ratio of the gas constant water 0.4615 kJ / kg.K, w = - 290 kJ / kg (100%) assumption total water content approx. 5% (with increasing way as gas, therefore about half of the gas volume over total compression ) - 290 kJ / kg x 0.025 = 7.2 kJ / kg
    Total compaction: 180.5 kJ / kg + 7.2 kJ / kg = 187.7 kJ / kg
    Compaction air for cooling air requirement approx. 5% and mass supply wood approx. 3.5% = 187.7 kJ / kg x 1.085 = approx. 205 kJ / kg
    Hot air motor: (5% water vapor from compression + approx. 1.5% water vapor from heat surplus through additional residual heat gas mass from combustion and temperature difference at recuperator outlet + approx. 3.5% additional effective mass through wood pulp from combustion, where additional air mass can be heated, but also the corresponding air has to be compressed)
    Use polytropic exponent (n = 1,34 ... flue gas practically present) instead of isentropic exponent (kappa 1,4 air)
    Working gas temperature 850 ° C, system pressure 7 bar abs. Zellenradmotor
    Isobaric heat supply: qzul2 = cpml2 x (TI - T2)
    Temperature End Polytrope Expansion: T2 = TI x (p2 / pl) high n - 1 / n (0.2537)
    1123 x 1/7 high 0.2537 = 685 K = 412 ° C cpml2 = (cpml x tl) - (cpm2 x t2) / (tl -12) = 1.077 kJ / kg.K x 850 ° C -1.030 kJ / kg.K x 412 ° C / (850 ° C - 412 ° C) = 491/438 = 1.121 kJ / kg.Kqzul2 = cpml2 x (T1 - T2) = 1.121 kJ / kg.K x 438 K = 491 kJ / kg = wl2
    Heating and expansion with 5% water vapor ratio in relation to the specific heat capacity = x 2 qzul2 water vapor = 491 kJ / kg x 0.05 x 2 = 49.1 kJ / kg
    Share of 3.5% mass feed by fuel = 491 kJ / kg x 1.035 = 508 kJ / kg Total: 508 kJ / kg + 49 kJ / kg = 557 kJ / kg, compression 205 kJ / kg
    Efficiency = useful work amount of heat supplied
    Expansion work - compression work supplied heat
    Efficiency: (557 kJ / kg - 205 kJ / kg / (558 kJ / kg) = 352 kJ / kg / 557 kJ / kg = 0.632
    Approximate consideration of the isentropic efficiency and heat transfer to the cylinder wall with labyrinth seals approx. 0.92 557 kJ / kg x 0.92 = 512 kJ / kg, difference 44.5 kJ / kg
    Theoretical efficiency with reduction present: 512 kJ / kg-205 kJ / kg / 512 kJ / kg = 307 kJ / kg / 512 kJ / kg = 0.599
    Gas flow heating: is normally identical to the expansion work of the isentropic and / or the polyropyne and the equal pressure component at the gas inlet and isobaric gas flow heating. Here it is to be considered that the supplied fuel (about 3.5% by weight) also has a heating requirement of 30 ° C to ca. 412 ° C with approx. 10 kJ / kg (calculated in the fuel component heating requirement above) has an effect of increasing the heat input by 3.5% as the expansion work is taken into account. With the recuperator a temperature difference (about 35 ° C) with approx. 35 kJ / kg is to be considered, therefore the total heat requirement at
    Cell-wheel motor isobaric heat supply up to 850 ° C, (polytropic exponent n = 1.34 and moisture remains in air flow) 512 kJ / kg-205 kJ / kg / (512 + 35 kJ / kg + 10 kJ / kg) - 307 kJ / kg / 557 kJ / kg = 0.551
    Hot air motor isobar 850 ° C, (polytropic exponent n = 1.34, calculated no humidity in the air flow upon expansion) 508 kJ / kg x 0.92 = 467 kJ / kg 467 kJ / kg - 205 kJ / kg / 467 kJ / kg = 262 kJ / kg / 467 kJ / kg = 0.562 262 kJ / kg / (467 kJ / kg + 35 kJ / kg + 10 kJ / kg) = 262 kJ / kg / 512 kJ / kg = 0.512
    Cell wheel motor working gas temperature assumed 1200 ° C, (polytropic exponent n = 1.34 and moisture remains in air flow)
    Isobaric heat supply: qzul2 = cpml2 x (TI - T2)
    Temperature End Polytrope Expansion: T2 = TI x (p2 / pl) high n - 1 / n (0.2537)
    1473 x 1/7 high 0.2537 = 899 K = 626 ° C cpml2 = (cpml x tl) - (cpm2 x t2) / (tl -12) = 1.11 kJ / kg.K x 1200 ° C -1.055 kJ / kg.K x 626 ° C / (1200 ° C - 626 ° C) = 672/574 = 1.17 kJ / kg.Kqzul2 = cpml2 x (T1 - T2) = 1.17 kJ / kg.K x 574 K = 672 kJ / kg = wl2
    Heating and expansion with 5% water vapor ratio in relation to the specific heat capacity = x 2 qzul2 water vapor = 672 kJ / kg x 0.05 x 2 = 67.2 kJ / kg
    Share of 3.5% mass feed by fuel = 672 kJ / kg x 1.035 = 695 kJ / kg Total: 695 kJ / kg + 67.2 kJ / kg = 762.2 kJ / kg, compression 205 kJ / kg
    Efficiency = useful work amount of heat supplied
    Expansion work - compression work supplied heat
    Efficiency: (762 kJ / kg - 205 kJ / kg / (762 kJ / kg) = 557 kJ / kg / 762 kJ / kg = 0.731
    Approximate consideration of the isentropic efficiency and heat transfer to the cylinder wall with labyrinth seals approx. 0.92 762 kJ / kg x 0.92 = 701 kJ / kg, difference 61 kJ / kg
    Theoretical efficiency with reduction and heating requirement / temperature difference Recuperator: 701 kJ / kg - 205 kJ / kg / (701 kJ / kg + 45 kJ / kg) = 496 kJ / kg / 746 kJ / kg = 0.665 Assumed isothermal expansion at 800 ° C and 7 bar abs. W = R x T x ln pl / p 2 = 0.2872 kJ / kg.K x 1073 K x ln 7/1 = 599.6 kJ / kg (t = 20 ° C)
    Water vapor content 5% 0.4615 x 1073 x ln 7 = 963.5 kJ / kg x 0.05 = 48 kJ / kg Total: 647.7 kJ / kg
    Assumed 5% loss due to friction and heat loss: 615.4 kJ / kg efficiency with humidity 615.4 kJ / kg - 205 kJ / kg = 410.4 kJ / kg / 615.4 kJ / kg = 0.667 efficiency without moisture: (599.6 - 5%) 569.6 kJ / kg - 205 kJ / kg = 364.6 kJ / kg / 599.6 kJ / kg = 0.608
    Efficiency at 0.5 bar Pressure loss at 850 ° C and humidity present: 512 kJ / kg - 212 kJ / kg = 300 kJ / kg / 557 kJ / kg = 0.539 x 0.95 (current) = 0.512
    Efficiency at 0.5 bar Pressure loss at 850 ° C and no moisture present: 467 kJ / kg - 212 kJ / kg = 255 kJ / kg / 512 kJ / kg = 0.498 x 0.95 (flow) = 0.473
    Efficiency at 0.5 bar Pressure loss at 1200 ° C and humidity present: 701 kJ / kg - 212 kJ / kg = 489 kJ / kg / 746 kJ / kg = 0.655 x 0.95 (current) = 0.622
    Efficiency at 0.5 bar Pressure loss at 1200 ° C and no moisture present: 639 kJ / kg - 212 kJ / kg = 427 kJ / kg / 684 kJ / kg = 0.624 x 0.95 (flow) = 0.593
    Efficiency at 0.5 bar Pressure loss with isothermal expansion at 800 ° C and moisture present: 615.4 kJ / kg - 212 kJ / kg = 403.4 kJ / kg / 615.4 kJ / kg = 0.655 x 0.95 (current) 0.622
    Efficiency at 0.5 bar pressure loss with isothermal expansion at 800 ° C and no moisture present: 569.6 kJ / kg - 212 kJ / kg = 357.6 kJ / kg / 569.6 kJ / kg = 0.628 x 0.95 ( Current) = 0.593
    Mass flows at respective outlet temperatures 1 bar abs. / 7 bar without moisture 412 ° C: v = 1.94 m3 / kg, mass flow: 0.346 kg / sec at 750 rpm, current: 83.8 KW (850 ° C) 626 ° C: v = 2.55 m3 / kg, mass flow: 0.263 kg / sec at 750 rpm, current: 107 KW (1200 ° C)
    800 ° C: v = 3.05 m3 / kg, mass flow: 0.22 kg / sec at 750 rpm, current: 78.8 KW (800 ° C) isothermal expansion with humidity: 88.7 KW; at 1000 rpm = 118.3 KW
    Isothermal expansion without moisture: 78.8 KW; at 1000 rpm = 105.1 KW
    Speed 750 rpm: 103.8KW (850 ° C) 128.6KW (1200 ° C) humidity
    Heating power m. Humidity 194,4 KW 196,2 KW
    Without humidity: 83.3 KW (850 ° C), 107 KW (1200 ° C)
    Heating power or humidity 177 KW 179.8 KW
    Speed 1000 rpm: 138.4 KW (850 ° C), 171.4 KW (1200 ° C) humidity
    Heating power m. Humidity 259.6 KW 261.6 KW
    Without humidity: 111 KW (850 ° C), 142.6 KW (1200 ° C)
    Heat output or humidity 236 KW 239.7 KW (Note: The permissible speed of the rotary vane motor depends on the size, smaller units up to about 1500 rpm, medium and larger about 750 to 1000 rpm), a size with double dimensions As stated at the beginning, the useful power would range from about 700 to 800 KW.
    The achievable efficiency with the moisture content in the working gas is at the respective temperatures by about 4% abs. higher compared to working gas without moisture content, The efficiency also increases with the working gas temperature by about 5% per 100 ° C higher working gas temperature. Selected due to the technical requirements system pressure 7 bar, working gas temperature about 800 to 850 ° C with introduction of heat through high-temperature heat exchanger, beyond this temperature is possible only by direct introduction of the fuel into the working gas.
    Heat of condensation for district heating: (from approx. 85 ° C to approx. 30 ° C) 0.05 x 2653 kJ / kg + 358 kJ / kg = 491 kJ / kg0.01 x 2556 kJ / kg + 313 kJ / kg = 338 kJ / kg of enthalpy difference: 152 kJ / kg
    This heat of condensation after compression is usable for space heat recovery. The achievable overall efficiency with cellular motor is about 40 to 50% at a working gas temperature of about 850 ° C and about 50 to 60% at working gas temperature of about 1200 ° C or isothermal-like expansion. To account for the generator efficiency, 0.95 was used. The total utilization rate of complete heat utilization is about 85%. When using a system pressure with 8bar abs. with the working gas temperature of 850 ° C, the exit temperature, depending on the proprolyte exponent, is about 350 ° C, which could be used to cool the enclosure.
    权利要求:
    Claims (9)
    [1]
    1. Cellular motor for stationary use according to the basic principle of a slat compressor with a rotor mounted eccentrically to the housing axis (4) with radially movable cell walls (6), which in a groove in the side walls (8) via 2 each with rollers (7) provided Bolt be forced and thus made no contact with the housing wall (9), characterized in that the rotation resulting on expanding cell volume for the introduction of the hot and pressurized working gas over a tuned angle of rotation is used and is relaxed under utilization of power to ambient pressure.
    [2]
    A stationary-use cell-wheel motor according to claim 1, characterized in that the positively driven cell walls (6) are also supported in the grooves of the rotor (4) for minimizing friction in the radial direction by means of rolling elements (21) which are functionally similar to rolling bearings Cage (22) are guided.
    [3]
    3. cell wheel motor for stationary use according to claim 1 to 2, characterized in that the cell walls (6) are provided to the housing (9) out with a labyrinth seal (15) in order to minimize the gap losses.
    [4]
    4. cellular motor for stationary use according to claim 1 to 3, characterized in that two strips per cell wall (6) with a labyrinth seal on the rotor circumference (15) are provided, which takes over the working gas in the cell sealing towards the rotor gaps.
    [5]
    5. Stationary cell wheel motor according to claim 1 to 4 characterized in that the space between the rotor (4) and inner radius of the cell guide by means of insulation (25) is provided to the heat flow from the working gas in the cells to the rotor (4) as possible to keep small.
    [6]
    6. Zellenradmotor for stationary use according to claim 1 to 5, characterized in that the leading edge for the working gas is adjustable to the housing to introduce at different pressures that volume of gas, which corresponds to complete relaxation of the ambient pressure.
    [7]
    7. cell wheel motor for stationary use according to claim 1 to 6, characterized in that via a side wall (14) by means of a bore and the gap between the rotor (4) and wall, bounded by plates upper half that amount of cooling air is introduced, which for the cooling the cell walls (6) and the rotor (4) are required, separately from which the cooling air supply for the pins of the force guide with storage of the cell walls.
    [8]
    8. stationary motor according to claim 1 to 7, characterized in that that groove in the side walls (8), which takes over the forced guidance of the cell walls (6) to minimize the gap to the housing wall (9), which of the eccentricity and Width of the labyrinth seal on complex relationships of the angle functions and with the changing angle of rotation depends, is designed so that thereby the gap is minimized by the individual points of the curve are traced with a CNC milling machine.
    [9]
    9. A stationary stationary electric cell motor, characterized in that the motor is used as a compressor or vacuum pump where the same direction of rotation causes the inlet (26) and outlet (27) to be mirror images, or if the direction of rotation is reversed, the opening angles remain on the same sides, for the same diameter, the length is determined according to the specific volumes of lean working gas and intake air for the compressor
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    同族专利:
    公开号 | 公开日
    AT514998B1|2015-09-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE4429877A1|1993-02-13|1996-02-15|Irm Antriebstech Gmbh|Heat engine with rotor and cells|
    WO1995035431A1|1994-06-20|1995-12-28|Edwards Thomas C|Non-contact rotary vane gas expanding apparatus|
    WO2000052306A1|1999-03-01|2000-09-08|Mallen Brian D|Vane pumping machine utilizing invar-class alloys for maximizing operating performance and reducing pollution emissions|
    WO2007063357A1|2005-11-29|2007-06-07|Michael Stegmair|Vane-type machine and method of utilizing waste heat while using vane-type machines|
    AT518480A1|2016-04-06|2017-10-15|Walter Falkinger Ing|Zellenradmotor|
    法律状态:
    2020-08-15| MM01| Lapse because of not paying annual fees|Effective date: 20191018 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA803/2013A|AT514998B1|2013-10-18|2013-10-18|Zellenradmotor|ATA803/2013A| AT514998B1|2013-10-18|2013-10-18|Zellenradmotor|
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