WO2009049344A2 - Centrale thermique pour la production combinée d'énergies thermique et mécanique - Google Patents

Centrale thermique pour la production combinée d'énergies thermique et mécanique Download PDF

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Publication number
WO2009049344A2
WO2009049344A2 PCT/AT2008/000376 AT2008000376W WO2009049344A2 WO 2009049344 A2 WO2009049344 A2 WO 2009049344A2 AT 2008000376 W AT2008000376 W AT 2008000376W WO 2009049344 A2 WO2009049344 A2 WO 2009049344A2
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WO
WIPO (PCT)
Prior art keywords
piston
rotor
cylinder
steam
power plant
Prior art date
Application number
PCT/AT2008/000376
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German (de)
English (en)
Other versions
WO2009049344A3 (fr
Inventor
Klaus VÖLKERER
Willibald Eidler
Arno Past
Josef Koglbauer
Original Assignee
Voelkerer Klaus
Willibald Eidler
Arno Past
Josef Koglbauer
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
Application filed by Voelkerer Klaus, Willibald Eidler, Arno Past, Josef Koglbauer filed Critical Voelkerer Klaus
Publication of WO2009049344A2 publication Critical patent/WO2009049344A2/fr
Publication of WO2009049344A3 publication Critical patent/WO2009049344A3/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]

Definitions

  • the invention relates to a thermal power plant for the combined generation of thermal and mechanical energy, which plant has a steam generator, a condenser, a feedwater pump and the pressure gradient between the steam generator and the condenser a mechanical output shaft driving engine.
  • EP 1 405 987 A1 discloses a thermal power plant for generating mechanical energy, which plant has a steam generator, a condenser, a feed water pump and, in the pressure gradient between the steam generator and the condenser, an engine driving a mechanical output shaft.
  • the engine is an axial piston engine, wherein on the side facing away from the piston rotor side of the cylinder rotor in the adjacent thereto wall the motor housing in the trajectory of the Zylinderöffhungen separated from each other, an inlet opening and an outlet opening are provided, and wherein the inlet opening is connected to the working pressure under pressure vapor phase of the steam generator and the outlet opening connected to the normal or negative pressure vapor phase of the condenser.
  • the pistons of the axial piston motor are subjected to pressure during the working cycle.
  • Output shaft driving engine has.
  • the engine is an axial piston engine, wherein on the side facing away from the piston rotor side of the cylinder rotor in the adjoining wall of the motor housing in the trajectory of the cylinder openings separated from each other
  • Inlet opening and an outlet opening are provided, and wherein the inlet opening with the under
  • Capacitor and having a mechanical output shaft driving engine in the pressure gradient between the steam generator and the condenser is a piston engine, but WO 1989/07699 A1 does not describe an axial piston engine.
  • JP 2005337066 A relates to a thermal power plant for generating mechanical energy, which plant a steam generator, a condenser, a feedwater pump and in
  • Output shaft driving engine has.
  • the engine is an axial piston engine.
  • the pistons of the axial piston motor are controllably loaded to pressure.
  • GB 785 035 A discloses a thermal power plant for generating mechanical energy, which plant a steam generator, a condenser, a feedwater pump and in
  • Output shaft driving engine has.
  • a steam turbine is provided.
  • the present invention is intended to enable a novel heat engine, which reduces the above disadvantages and also allows for a better energy balance in smaller installations, such as combined heat and power plants or small and micro-cogeneration plants, as corresponding systems of the prior Technology. These goals are achieved by a thermal power plant in that the engine
  • Axial piston engine is, whose turned towards the piston rotor, located behind the cylinder rotor mecanicraurn with the steam generator is in communication and with a working pressure under liquid phase of a working medium, preferably under working pressure liquid phase of the working medium of the steam generator is filled, wherein on the side facing away from the piston rotor side of the cylinder rotor in the adjoining wall of the motor housing an inlet opening and an outlet opening are provided separately in the trajectory of the cylinder openings, and wherein the inlet opening is connected to the steam phase of the steam generator under working pressure and the outlet opening is connected to the vapor phase of the condenser which is under normal or negative pressure.
  • wet steam in the cylinder is thus unproblematic in the present invention, whereby it is possible to operate the engine with steam of different and low quality, without damaging the engine.
  • the liquid phase of the working medium under working pressure acts on the piston side facing the piston rotor (hereinafter "piston underside") as a lubricant which permits oil-free operation of the engine without the need for special high-performance materials such as carbon and ceramic.
  • the demands placed on the cylinder seals are small, since small amounts of working medium can flow from the liquid phase past the piston bottom past the piston to the vapor phase, without this significantly restricting the operation of the engine or even damaging it.
  • the wall of the motor housing resting against the cylinder rotor may be formed by a control disk fixed to and covering the cylinder rotor and having at least one inlet opening and one outlet opening, the cylinder bores depending on the cylinder bore Rotary position of the cylinder rotor open either in the inlet opening of the control disc, open in the outlet of the control disc, or are sealingly covered by the control disc.
  • the control disk is thus easily replaceable on the one hand as a wearing part and on the other hand it is possible to use different control discs, which allow by changing the dimensions of the openings to adapt the engine to different working conditions.
  • control disk may have four successive angular ranges, a steam inlet region having the inlet opening, a sealing expansion region, a steam outlet or working stroke region having the outlet opening, and an empty region between outlet opening and inlet opening.
  • a steam inlet region having the inlet opening
  • a sealing expansion region having the outlet opening
  • a steam outlet or working stroke region having the outlet opening
  • an empty region between outlet opening and inlet opening.
  • control disk may have a condensate return passage in the empty area between the outlet opening and the inlet opening. This eliminates the need to provide a separate condensate pump.
  • This design maximizes the length of the working cycle while allowing for a sufficiently large relaxation area to relax the steam according to the conditions of use.
  • the axis of rotation of the cylinder rotor can enclose an angle between 2 ° and 7 °, preferably 5 °, with the axis of rotation of the piston rotor.
  • a small angle makes it possible to form the piston rods on the piston rotor only with little play, or to attach these fixed to the piston rotor.
  • the bending forces in the piston rods which result from the difference between the circular movement of the pistons in the piston rotor and the elliptical movement of the pistons in the cylinder rotor, could be absorbed by the elasticity of the piston seals. This is possible because the game is very small at a small angle, and since the piston seals in the cylinder need not be absolutely tight according to the invention. Since in the machine according to the invention, the pistons in each power stroke exclusively on
  • the piston rods of the axial piston machine can pass through holes or recesses in the piston rotor through the latter, wherein the piston rods on the side facing away from the cylinder rotor of the piston rotor, by a widening in the form of a bolt head, a nut, or the like a withdrawal are secured.
  • compression springs may be arranged on the piston rods between the piston rotor and the piston.
  • the cylinder rotor can be mounted floating in the motor housing. This is possible because the cylinder rotor is pressed by the working pressure of the liquid phase of the working medium in the interior against the control disk and moved by pulling action of the piston rods with the piston rotor and automatically runs synchronously.
  • the mechanical output can in preferred embodiments of the invention a
  • thermoelectric Generator a heat pump, a compressor, a conveyor, a (feedwater) pump or drive a combination of these devices in order to adapt the thermal power plant according to the invention to a variety of different working and environmental conditions.
  • each cylinder bore circle on a control disk is associated with an inlet and an outlet and wherein the inlet of the first cylinder bank with the Inlet port of the axial piston motor is in communication, the outlet of the last row of cylinders is in communication with the outlet opening of the axial piston motor, and the outlets of the other rows of cylinders are in each case in communication with the inlet of the nearest row of cylinders.
  • connection between successive rows of cylinders can be integrated in the control disk, or be led out of the housing, for example, to branch off steam of a medium expansion stage.
  • a further optimization of the system according to the invention can be achieved by providing an additional piston crown as a condensate pump.
  • the piston crown which acts as a condensate pump, the positions of the inlet and outlet ports are reversed so that this ring acts not as a motor but as a pump.
  • a regenerator may be provided, which is designed as a heat exchanger between the emerging from the axial piston motor under normal or negative pressure vapor phase of the working medium and leading to the steam generator feedwater.
  • FIG. 1 shows a cross-sectional view of an axial piston motor of the heat engine according to the invention mounted between the steam generator, condenser and generator,
  • Fig. 2 is a sectional view of the axial piston motor along the line U-II of Fig. 1
  • Fig. 3 is a perspective view of the system shown in Fig. 1
  • Fig. 4 is a plan view of the system shown in Fig. 1
  • FIG. 5 is a schematic representation of the control disk of the axial piston engine, which is the
  • FIG. 6 is a perspective view of the control disk of FIG. 5; FIG.
  • FIG. 7 is a perspective view of the piston rotor with the pistons attached thereto
  • Fig. 8 is a perspective view of the cylinder rotor
  • Fig. 9 is a perspective view of a control disk without Dampfentschreib with
  • FIG. 10 and Fig. 11 show a schematic representation of two rotatable discs in a plan view and side view to illustrate the operation of the axial piston motor according to the invention, the axes of rotation enclose an angle and between which a tension spring in a position A and a position B is shown,
  • FIG. 12 is a schematic representation of the elements of the thermal power plant for explaining the sequence of piston positions in one revolution of the engine, wherein the circular path of the piston is shown as a development in a plane,
  • FIG. 13 is a schematic representation of a control disk for an axial piston engine with two concentric piston rings and two expansion stages
  • Fig. 14 is a plan view of a cylinder rotor with two concentric cylinder rings, which can be used with the control disk of Fig. 13, and
  • Fig. 15 is a block diagram of a plant according to the invention which uses a regenerator for feedwater preheating.
  • FIGS. 1 to 4 An embodiment of the inventive thermal power plant is shown in FIGS. 1 to 4 in various views and sections.
  • the plant described uses water vapor as a working medium, but it can also be another medium, which has a suitable change between vapor phase and liquid phase, are used with a system according to the invention.
  • An axial piston motor 1 according to the invention is mounted on a holder 4 and drives a generator 3 via a V-belt 5.
  • the motor could drive other units, for example a heat pump, a compressor, a (feed water) pump, a conveyor or a combination thereof institutions.
  • the steam required for the operation of the engine is generated in a steam generator 2 and fed via a steam line 6 (FIGS. 2 to 4) to the axial-piston engine 1.
  • a pressure equalization line 7 and a feedwater line 8 leads from the steam generator 2 to the axial piston motor 1.
  • the condenser line 9 leads from the axial piston motor 1 to a condenser 10.
  • the heat released during the condensation in the condenser is supplied to a heating system via a heating flow and return.
  • the condenser may be of known type, with a peculiarity of the system according to the invention is that condensate, which runs from the condensate line 9 back into the engine, can be automatically discharged into the engine compartment, and via the feedwater pipe. 8 gets back into the steam generator 2, as will be explained below.
  • the condensate can also be fed back into the steam generator in a conventional manner via a feedwater pump.
  • the core of the thermal plant is the axial piston motor 1, which is shown in Fig. 1 and 2 in a respective sectional view.
  • the motor is surrounded by a motor housing 21, which is substantially cylindrical, and is closed at the top and bottom by housing covers 22, 23.
  • the axial piston motor 1 is attached to the lower housing cover 23 to a bracket 4 and has below a central opening through which an output shaft 14 passes. The opening is sealed by means of a mechanical seal 15 with respect to the output shaft 14.
  • the output shaft is rotatably mounted on two shaft bearings 18 and at its upper end in the motor interior 20, a piston rotor 12 is mounted. At its lower end, the output shaft 14 is connected via the V-belt 5 to the generator 3.
  • piston rods 17 are arranged in a radius around the axis of rotation, as shown diagrammatically in Fig. 7.
  • each piston rods 17 At the upper end of each piston rods 17 each have a piston 16 is attached.
  • the piston rods are inserted into bores in the piston rotor 12 and have at their lower end a head with an enlarged cross section.
  • the piston rods 17 are inserted from below through the holes in the piston rotor 12 until its head rests against this, and then the piston 16 is fastened to the piston rod.
  • a piston spring 19 is pushed onto the piston rod 17, which pushes the piston 16 away from the piston rotor 12, and thus prevents the piston rod from slipping down through the bore in the piston rotor. Since the piston rods, as will be explained in more detail later, are loaded only on train during engine operation, the piston springs 19 do not absorb large forces and are mainly used for stability at standstill.
  • the holes may also have a clearance relative to the piston rods 17, so that the piston rods 17 can be pivoted slightly at a corresponding angle.
  • the pistons 16 are screwed on the piston rods 17 in the illustrated embodiment, but the attachment can also be carried out in another known manner, such as by means of a press fit, a lock nut, a retaining ring, etc.
  • the pistons 16 have an approximately diskus- or lens-like shape, wherein they have at their periphery a groove in which a piston seal 28 is arranged.
  • Each piston moves in a separate cylinder bore 27 of a cylinder rotor 11, which is shown diagrammatically in Fig. 8.
  • the cylinder rotor 11 is pressed by the pressure in the engine compartment 20 up to a control disk 13, as will be explained in more detail.
  • a retaining pin 24 which protrudes centrally from the piston rotor 12 and ends with a ball-like head end in a central recess of the cylinder rotor 11, serves to secure the cylinder rotor 11 even when the engine is against falling down, and to the Cylinder rotor 11 to center in its axis of rotation.
  • the cylinder rotor 11 is floating and it is also not necessary to match the rotation of the piston rotor 12 and the cylinder rotor 11 (such as by means of a toothing, a transmission or a Kardanitati), since the cylindrical rotor 11 due to the kinematic Conditions always with the rotating piston 16, and thus moved with the piston rotor 12, as will be explained in more detail.
  • the control disk 13 above the cylinder rotor 11 is fixedly connected to the motor housing 21, thus stands still while the cylinder rotor 11 rotates underneath.
  • the motor interior 20 of the axial piston motor 1 is connected to the upper housing cover 22 via the pressure equalization line 7 with the vapor phase in the upper region of the steam generator 2, and on the lower housing cover 23, the motor interior 20 via the feedwater line 8 with the liquid phase in the lower region of the steam generator 2 connected.
  • the steam generator is partially filled with boiler water 25, wherein the water surface is shown by the dashed line in Fig. 1. Through the boiler water 25 run flue pipes 26, through which the water is heated to produce steam that collects above the water surface.
  • the axial piston motor 1 is arranged below the surface of the boiler water, so that the motor interior 20 is filled due to the principle of communicating vessels with boiler water, which thus has the same working pressure, as the steam generator 2.
  • the pressure equalization line 7 is essentially a flow of working fluid instead of.
  • the mass flow with which the axial piston motor 1 is driven is supplied via the steam line 6 (FIGS. 2 to 4) to the axial piston motor 1 as superheated steam under working pressure, and discharged to the condenser 10 via the condenser line 9 as a relaxed, cooler steam at low pressure. From there, the condensate passes through a feedwater pump (this is not shown in Fig. 1-4, but it essentially corresponds to the feedwater pump 43, which is shown schematically in the block diagram of Fig. 15) back into the boiler 2.
  • condensate which the condensate line 9 runs back into the engine, is discharged via a condensate return passage, or fed back into the engine compartment 20, as will be highlighted in more detail with reference to the other figures in the sequence.
  • Liquid working medium which passes through leaks, such as at the piston seal 28 or the edge of the cylinder rotor 11, in the drive mass flow, either mixed with the (steam) mass flow or it is treated in the same way as the condensate ,
  • the axis of the piston rotor 12 and the axis of the cylinder rotor 11 are at a small angle ⁇ (approximately between 2 ° and 7 °, in this case approximately 5 °) °) are arranged to each other, so that the cylinder rotor 11 and the piston rotor 12 at the right with respect to FIG. 1 motor side due to the inclination have a smaller distance from each other than on the opposite side. Therefore the right in Fig. 1 piston is very deeply inserted into its cylinder bore 27 so that only a minimal or no volume above the piston remains, and the left in Fig.
  • each piston sucks working fluid as it passes the inlet and ejects it on the opposite side at the outlet again.
  • This operation is very similar to conventional axial piston machines, but when operating the axial piston engine according to the invention as an engine, some special features are to be considered, which will be discussed below.
  • each piston rod 17 does not remain straight in one revolution of the piston rotor 12 with respect to the piston rotor 12, but "wobbles.”
  • this wobble is relatively small, and may be accompanied by a corresponding clearance the attachment of the piston rods 17 on the piston rotor 12 on the one hand and by elastic deformation of the piston seals 28 in the cylinder rotor on the other hand be compensated
  • the piston rods 17 instead of the piston rods 17, to use ropes or in the piston rods 17 near the piston rotor 12 a joint which allows the tumbling movements, the steam flowing over the da Mpftechnisch 6 is supplied to the axial piston motor 1, reaches the control disc 13, which serves to the steam in the right places to the underneath rotating To guide cylinder bores.
  • FIG. 9 shows a schematic plan view of the control disk of Fig. 6, wherein the underlying cylinder bores are shown in dashed lines, and the individual work cycles are indicated.
  • the control disk 13 of FIG. 9 has, on the cylinder cover surface 32 facing the cylinder rotor, two arcuate passages or grooves, one of which serves as an inlet opening 29 and the other as an outlet opening 30. At the rear of the control disk 13, a hole can be seen behind each groove, via which the connection to the steam line 6 and the capacitor line 9 is produced. The inlet opening 29 is thus connected to the steam line 6, and the outlet opening 30 opens into the condenser line 9. Between the outlet opening 30 and the inlet opening 29, a condensate return channel 31 is further introduced. If the control disk of FIG. 9 is installed in the axial-piston engine 1 (FIGS.
  • the pressure in the engine compartment 20 is slightly higher than the pressure of the hot steam of the steam generator applied to the inlet opening 29 at the piston top. It is due to this pressure difference that the piston rods 17 are always loaded with tension in each circulating position, the pistons communicating with the inlet opening 29 exert only a slight pull (due to the small pressure difference), and the pistons are in connection with the outlet 30, due to the high pressure difference between the capacitor line 9 and the motor interior 20 are pulled up strongly.
  • the liquid working fluid in the motor interior 20 also serves to lubricate the moving parts, so that oil-free operation is ensured, moreover, the pressurized working fluid in the engine compartment 20 presses the cylinder rotor 11 upwards against the control disk 13, so that no expensive to hold the cylinder rotor 11 Bearings are required. It is sufficient to center the cylindrical rotor 11 in its axis of rotation, which takes place in the illustrated embodiment on the retaining pin 24.
  • a further advantage of the working fluid in the motor interior 20, which is under working pressure, is that the pistons 16 and the cylinder rotor 11 do not have to be absolutely tight, since the same medium is located on both sides of the piston, albeit in a different state of aggregation. Now get at leaks small amounts of the liquid working medium in the vapor region at the piston top (this is especially in the range of the low pressure outlet port 30 to be expected), then they either evaporate and combine with the steam, or they form condensate is excreted again at the top dead center via the condensate return passage 31 together with the condensate returning from the condenser. Because of these low demands on the tightness of the engine can be operated with low-quality steam or wet steam, which would quickly damage the high-quality piston seals or the turbine blades in conventional steam engines or turbines.
  • Fig. 10 and U show in a plan view and a side view of two superimposed, rotatably mounted discs 33, 34 whose axes of rotation are arranged at an angle ß to each other.
  • the inclination angle ß of the discs 33, 34 shown in the figures exaggerated to illustrate the operation. If now from point A of the upper disc 33 from a tension spring (or an elastically stretched rubber band) stretched to the underlying point A 'of the lower disc 34, so both discs will rotate simultaneously due to the applied tensile force, until the spring 35 from the point A has moved to the point B, at which the distance between the two suspension points BB 'is minimal.
  • the same principle also causes the rotation of the axial piston motor 1 according to the invention, wherein the point A corresponds to the point at which the cylinder bore in the cylinder rotor 11 with the outlet opening 30 in the Control disc comes into connection, so that due to the pressure difference, a high tensile force is applied to the piston rod. Even before the bottom dead center (in the model of FIGS. 10 and 11, this would correspond to the point B), the cylinder bore is separated from the outlet opening 30, so that only small tensile forces act on the piston rod, so that the rotors due to the always new in the area of the outlet opening 30 reaching cylinder continues to rotate.
  • FIG. 9 Another preferred embodiment of the invention uses a control disk 13 as shown in FIG.
  • the difference with respect to the control disk 13 in Fig. 9 is that the inlet port 29 is made much smaller, so that essentially always only one cylinder is simultaneously in communication with the steam inlet.
  • an area is created between the inlet opening 29 and the outlet opening 30 in which the cylinders are covered by the cylinder top surface 32. Since this cover takes place in an area where the volume increases, the vapor taken in the inlet port 29 is released before the piston reaches the outlet port 30, and the power stroke starts.
  • Fig. 5 shows a plan view of the control disk 13, wherein the individual angular ranges are located.
  • the direction of rotation runs from top dead center (TDC - minimum volume), via the steam inlet area (I), the expansion area (H), the bottom dead center (UT - maximum volume), the steam outlet or working rate range (III) and back to TDC a condensate return channel 31 is located (TV).
  • the length of the inlet opening 29 can be adjusted in accordance with the system parameters by means of selected control disks so that the pressure gradient between the superheated steam and the condenser which is suitable for the system is achieved.
  • Fig. 12 shows a development in a diagrammatic representation strung together the individual positions, which passes through a piston 16 during a revolution of the cylinder rotor 11.
  • the piston sucks superheated steam out of the steam line 6 via the inlet opening 29 and the steam is expanded in the expansion area (H).
  • the steam can be fed directly from the steam generator.
  • a steam temperature of 250 C ° would result at a working pressure of 40 bar, for example, the temperature would be about 212 C ° at 20 bar and about 200 C 0 at 16 bar.
  • the steam can also be superheated before it is fed to the engine, whereby depending on the system steam temperatures between 350 and 600 C 0 , possibly even more, could be achieved.
  • the pistons in the steam outlet or working stroke range (IE) due to the high pressure difference between the condenser line 9 and the working pressure, located in the engine compartment 20 liquid working medium 25 is pushed upward, wherein the expanded steam is discharged to the condenser.
  • the pressure in the condenser could be 0.2 bar, in which case the relaxed steam leaves the engine at a temperature of about 60 ° C.
  • the pressure in the condenser can also be higher, which also results in a higher temperature for the steam supplied to the condenser. This higher temperature could for example also be used for a feedwater pre-heating, as described below in connection with FIG. 15.
  • the system can also be operated at different pressures and temperatures, with the corresponding pressures / temperatures being taken from steam tables or steam diagrams.
  • the condensate that has accumulated in the cylinder during the working cycle is pressed into the condensate return channel 31 in the condensate zone (FV).
  • the condensate return passage 31 could also open directly into the engine compartment 20. Due to the fact that a residual amount of condensate remains in the cylinder volume at top dead center, it is avoided when the piston stroke starts that a dead volume arises in this area, which would reduce the power of the engine.
  • the expanded steam is condensed, wherein a heating circuit is heated, which is indicated in the diagram by the heating flow 36 and the heating return 37.
  • a portion of the condensate passes through the condenser line 9 back into the engine, where it is discharged from the piston in the condensate return passage 31.
  • the rest of the condensate enters a downstream of the condenser feedwater pump, which feeds the condensate back to the steam generator.
  • all the condensate from the condenser can also run back into the outlet opening 30 of the axial piston motor 1 and be discharged into the condensate return channel 31 in the condensate region (IV).
  • the condensate return duct 31 introduce the condensate into the motor interior 20, from where it returns to the steam boiler 2 via the feedwater line 8.
  • no separate feedwater pump is required because the entire mass flow, which is supplied as steam via the steam line 6 to the engine, is discharged as condensate via the condensate return passage 31 back into the engine compartment 20.
  • the condensate, which is fed as feed water via the feedwater line 8 to the steam generator 2 can alternatively be warmed up by a feedwater preheating before it is fed to the steam generator 2.
  • Fig. 15 shows a block diagram of a thermal power plant according to the invention, wherein the
  • the System is equipped with a superheater 42 and a regenerator 41 for feedwater preheating.
  • the steam generated by the steam generator after being overheated in the superheater 42, is supplied to the axial piston motor 1. Thereafter, the expanded steam passes through a regenerator 41 to the condenser 10.
  • the regenerator is a conventional heat exchanger which further cools the steam before it is fed to the condenser.
  • the dissipated heat is used to heat the feedwater pumped by the feed water pump 43 before it is fed to the steam generator.
  • a plurality of concentric piston rings can be arranged on the piston rotor 1, corresponding concentric cylinder rings likewise being arranged in the cylindrical rotor 11.
  • Each piston crown acts like a separate axial piston engine with its own inlet opening 29, 29 'and outlet opening 30, 30' in a control disk 13, wherein a shared control disk can be provided.
  • Such a control disk 13 for two concentric piston rings is shown schematically in Fig. 13, wherein Fig.
  • FIG 14 shows a plan view of a cylinder rotor 11 with two concentric rings of cylinder bores 27, 27 ', which can be used with the control disk 13 of FIG ,
  • the steam is thereby relaxed in two stages, the Superheated steam is supplied to the inlet opening 29 of the inner piston crown via an inlet opening 38 leading to the steam line 6, and the pre-expanded steam is supplied to the inlet opening 29 'of the outer piston crown, which is discharged into the outlet opening 30 of the inner piston crown and via a connecting passage 40 of the inlet opening 29 'is supplied.
  • the steam is then further expanded, and discharged via the outlet opening 30 'of the second piston crown via an outlet opening 39 leading to the condenser line 9 to a condenser.
  • the control disk 13 may be formed as a simple disk on which the cylinder rotor side facing (the visible in Fig. 13 front), the inlet openings 29, 29 ', the outlet openings 30, 30' and the condensate return passage 31 are introduced as grooves or depressions.
  • the capacitor line 9 Toöffhung 39 and leading to the steam line 6 respectivelysöffhung 38 and the connecting passage 40 in the opposite side (the back in Fig. 13) of the control disk are introduced so that at the points where the recesses 29th , 29 ', 30, 30' at the front with the recesses 38, 39, 40 overlap at the back, a passage from the front to the back is created.
  • the mass flow transported via the individual piston rings must be coordinated to ensure optimum performance of both piston rotors.
  • the steam discharged from the outlet opening 30 of the inner piston crown can either be directed via the passage 40 shown in the figure to the inlet opening 29 'of the outer piston crown, or it can be guided via a conduit outside the housing, in both cases also a part can be removed from the pre-expanded steam, resulting in applications that previously only by steam turbines in large plants (where steam is tapped between individual turbine stages to feed about a feedwater or the like.) Or could be achieved by several series-connected units. Also, the steam could be in an intermediate superheater between the two
  • the axial piston motor according to the invention can also be operated as a pump by interchanging the inlet and outlet opening, it is possible in a further embodiment of the axial piston motor according to the invention

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  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne une centrale thermique destinée à la production combinée d'énergies thermique et mécanique, cette centrale comprenant un générateur de vapeur (2), un condensateur (10), une pompe d'alimentation et un moteur (1) situé dans la chute de pression entre le générateur de vapeur (2) et le condensateur (10). Ce moteur est un moteur à pistons axiaux (1) dont l'espace intérieur (20) faisant face au rotor à pistons (12) et situé à l'arrière du rotor à cylindres (11) est en communication avec le générateur de vapeur (2) et est rempli d'une phase liquide d'un fluide de travail (25), de préférence d'une phase liquide du fluide de travail du générateur de vapeur (2), cette phase liquide étant soumise à une pression de travail. Selon l'invention, un orifice d'admission (29) et un orifice d'échappement (30) séparés sont ménagés sur le côté du rotor à cylindres (11) opposé au rotor à pistons (12) dans la paroi du carter moteur (21), laquelle s'appuie contre le rotor à cylindres (11), dans la trajectoire des orifices cylindriques (27), l'orifice d'admission (29) étant relié à la phase vapeur du générateur de vapeur (2) qui est soumise à une pression de travail et l'orifice d'échappement (30) étant relié à la phase vapeur du condensateur (10) qui est soumise à une pression normale ou à une pression négative.
PCT/AT2008/000376 2007-10-17 2008-10-15 Centrale thermique pour la production combinée d'énergies thermique et mécanique WO2009049344A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA1672/2007 2007-10-17
AT16722007A AT505625B1 (de) 2007-10-17 2007-10-17 Wärmekraftanlage zur kombinierten erzeugung von thermischer und mechanischer energie

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WO2009049344A3 WO2009049344A3 (fr) 2010-07-01

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AT509207B1 (de) * 2010-05-19 2011-07-15 Klaus Ing Voelkerer Fluidenergiemaschine mit einem unter druck stehenden innenraum

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AT510720B8 (de) * 2011-03-02 2012-09-15 Klaus Ing Voelkerer Dampferzeugungseinrichtung

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US6152014A (en) * 1989-03-17 2000-11-28 Willimczik; Wolfhart Rotary piston machines
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Publication number Priority date Publication date Assignee Title
GB191200069A (en) * 1910-12-31 1912-12-23 Charles Richardson Pratt Improvements in Rotary Piston Engines.
DE2544179A1 (de) * 1974-12-20 1976-07-01 Gen Electric Integrierte elektrizitaetserzeugungs- und klimatisierungseinrichtung
EP0082671A2 (fr) * 1981-12-18 1983-06-29 TFC Power Systems Limited Conversion d'énergie thermique
US6152014A (en) * 1989-03-17 2000-11-28 Willimczik; Wolfhart Rotary piston machines
DE4411383A1 (de) * 1993-05-20 1994-11-24 Willimczik Wolfhart Drehkolbenmaschinen mit einem lagerfreien Kolbentriebwerk
WO1999036676A2 (fr) * 1998-01-14 1999-07-22 Yankee Scientific, Inc. Systeme de coproduction a petite echelle d'energie thermique et electrique
EP1405987A1 (fr) * 2001-07-10 2004-04-07 Honda Giken Kogyo Kabushiki Kaisha Dispositif a cycle de rankine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT509207B1 (de) * 2010-05-19 2011-07-15 Klaus Ing Voelkerer Fluidenergiemaschine mit einem unter druck stehenden innenraum
AT509207A4 (de) * 2010-05-19 2011-07-15 Klaus Ing Voelkerer Fluidenergiemaschine mit einem unter druck stehenden innenraum

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AT505625A4 (de) 2009-03-15
AT505625B1 (de) 2009-03-15
WO2009049344A3 (fr) 2010-07-01

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