EP2326821A2 - Machine thermique et procédé permettant de la faire fonctionner - Google Patents

Machine thermique et procédé permettant de la faire fonctionner

Info

Publication number
EP2326821A2
EP2326821A2 EP09740076A EP09740076A EP2326821A2 EP 2326821 A2 EP2326821 A2 EP 2326821A2 EP 09740076 A EP09740076 A EP 09740076A EP 09740076 A EP09740076 A EP 09740076A EP 2326821 A2 EP2326821 A2 EP 2326821A2
Authority
EP
European Patent Office
Prior art keywords
volume
heat engine
working medium
heat
heating
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP09740076A
Other languages
German (de)
English (en)
Inventor
Raimund WÜRZ
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE200810048641 external-priority patent/DE102008048641B4/de
Priority claimed from DE200810048633 external-priority patent/DE102008048633B4/de
Priority claimed from DE200810048639 external-priority patent/DE102008048639B4/de
Application filed by Individual filed Critical Individual
Publication of EP2326821A2 publication Critical patent/EP2326821A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/045—Controlling
    • F02G1/047—Controlling by varying the heating or cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/053—Component parts or details
    • F02G1/055—Heaters or coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2242/00—Ericsson-type engines having open regenerative cycles controlled by valves
    • F02G2242/02—Displacer-type engines
    • F02G2242/04—Displacer-type engines having constant working volume
    • F02G2242/06—Displacer-type engines having constant working volume with external drive displacers
    • F02G2242/10—Displacer-type engines having constant working volume with external drive displacers having mechanically actuated valves, e.g. "Gifford" or "McMahon engines"

Definitions

  • the present invention relates to a heat engine and a method for operating this heat engine.
  • an idealized comparison process is, for example, the Carnot process, which can take place both in the gas area and, in principle, also in the wet steam area of the state diagrams.
  • An isentropic compaction takes place in the Carnot process first, followed by an isothermal reversible energy transfer in the form of heat and work, followed by an isentropic decompression and finally an isothermal reversible energy transfer in the form of heat and work.
  • Another idealized comparison process is the so-called Joule process, which differs from the Carnot process in that the energy transfer is isobaric rather than isothermal.
  • the fourth idealized comparison process is the so-called Sstraer process, which was introduced specifically as a comparison process for cycles occurring in combustion engines (petrol and diesel engines).
  • Setzer process an isentropic compression of the working medium takes place first, followed by an isochoric reversible energy transfer in the form of heat, then an isobaric reversible energy transfer in the form of heat, then isentropic decompression and, finally, an isochronous reversible energy transfer in the form of heat.
  • the present invention proposes a heat engine according to claim 1 and a method of operating a heat engine according to claim 38.
  • a heat engine comprising a first volume arranged to be alternately heated and cooled, and also including a second volume, which is also arranged to be alternately heated and cooled. Furthermore, the heat engine comprises a working medium, which is contained in the first and in the second volume and a fluid line, via which the first volume and the second volume are interconnected. In this case, a machine operable with the working medium is connected between the first volume and the second volume with the fluid line.
  • the heat engine is further configured so that in a first state, the working fluid is heated in the first volume, while the working fluid is cooled in the second volume and in a second state the Working fluid is cooled in the first volume while the working fluid is heated in the second volume.
  • such a system can be adapted to a wide range of applications by appropriate choice of volumes and working medium.
  • helium as a working medium, for example, a high-temperature and high-pressure process can be realized in the temperatures up to several hundred degrees Celsius and pressures up to 300 or even 400 bar feasible are.
  • the above-described heat engine is also suitable to be operated with an ORC medium.
  • a phase transformation of the ORC medium for example the evaporation upon heating or the liquefaction upon cooling of the ORC medium, can take place.
  • a low-temperature ORC medium can be used, which evaporates just above room temperature, for example at 40 0 C.
  • the heat engine can be used in very different pressure and temperature ranges.
  • nitrogen or air can be used as environmentally neutral gaseous working media.
  • water vapor as an environmentally neutral working medium. In this case, a phase transformation between water vapor and liquid water occur.
  • mixtures of different working media can be used.
  • gas mixtures or mixtures of different ORC media can be used to suitably adjust the process parameters.
  • the heat engine described above can therefore be used in a variety of fields, namely wherever waste heat is available. In particular, this is, of course, in all combustion processes, for example. In engines, biogas combined heat and power plants, power plants, etc. the case. However, waste heat is also produced in many other technical processes, for example in steel production and processing, plastics processing and cement production. In all these processes, the heat engine can be used to harness the often wasted waste heat, save energy and increase the efficiency of the processes.
  • the pressure generator can also be used for the use of waste heat in heating systems in the living area, such as central heating or the like. In such systems, a burner temperature of 800-900 ° C is reached, with typical flow temperatures for space heaters are only 6O 0 C.
  • the high temperature difference can be made available by means of the pressure generator for power generation. Equally applicable is the above-described pressure generator in the field of combustion of renewable raw materials, in particular Holzpellet- or wood heating or fireplaces. The combustion of wood gas can also serve to generate the required waste heat.
  • the first and / or the second volume has a hot area and a cold area. That way that can alternating heating and cooling of the working medium in the respective volume can be ensured in a simple manner. Namely, the working medium will be provided in each case in the hot area or the cold area of the volume, depending on whether the working medium in this volume is just to be heated or cooled.
  • a coolant can be provided in the cold area.
  • a heating means may be provided in the hot area. Typically, the coolant and / or the heating means may be provided in respective heat exchangers.
  • both the first volume and the second volume may each have a first heat exchanger in the cold region and a second heat exchanger in the hot region.
  • first heat exchanger in the cold region
  • second heat exchanger in the hot region.
  • the respective first heat exchanger may each have a plurality of substantially parallel tubes for the coolant.
  • the respective first heat exchanger typically has a coolant inflow and a coolant outflow.
  • the respective second heat exchanger in each case a plurality of substantially parallel tubes for the heating means.
  • the second heat exchanger also each have a Schuffenzuhne and a Schuffenablig on. By arranging a plurality of parallel tubes, the surface available for heat exchange in the heat exchanger is increased.
  • a plurality of tubes with a relatively small cross section are arranged side by side and connected to one another, for example by welding.
  • a similar structure may be realized by providing a single larger rectangular profile into which partitions are inserted.
  • the advantage of such an arrangement is that due to the relatively small individual cross sections, the tubes are pressure-resistant with respect to the ambient pressures which occur, in particular, when the working medium is heated.
  • a respective heat exchanger can have a plurality of such tube bundles, which are arranged next to one another at a distance from one another. In this way, the working medium can flow into the interspaces between the respective tube bundles and absorb heat there from a heating medium on the surface of the respective tube bundles or emit heat to a coolant.
  • the hot and cold regions of a respective volume are thermally insulated from one another. In this way, an undesirable heat transfer from the hot area to the cold area can be reduced or avoided, so that the efficiency of the heat engine is increased.
  • the tubes of a first heat exchanger and the tubes of a second heat exchanger can be thermally insulated from each other by means of insulation.
  • a respective thermal insulation can be arranged between the tubes of the first heat exchanger and the tubes of the second heat exchanger.
  • the coolant inflow to the first volume and the coolant inflow to the second volume can be connected to a coolant line via a switch, wherein the switch is arranged to direct the coolant into either the first volume or the second volume.
  • the heating medium inlet to the first volume and the heating medium inlet to the second volume may be connected via a switch to a heating medium line, the switch being arranged to direct the heating medium into either the first volume or the second volume.
  • a single coolant stream or a single stream of heating medium can be conducted via the respective switches so that the coolant is only provided in each case in the volume in which the working medium is to be cooled, and the heating medium is provided only in the volume, in which the working medium is to be heated.
  • the respective heat exchangers in the cold or the hot region of a respective volume can only be charged with coolant or heating medium if this is actually required in this volume in the respective working cycle.
  • heating means or coolant are passed unused through a heat exchanger, because the heating means or the coolant in the respective clock in the volume just not needed.
  • the first heat exchanger and / or the second heat exchanger may each comprise a first group of pipelines and a second group of pipelines which are interconnected via a fluid connection.
  • the pipelines are arranged within the volume so that they are flowed through in opposite directions by the heating medium and / or the coolant.
  • a coolant or heating medium inlet may be provided at one end of the first group of pipes.
  • a coolant or Schuffenauslass may be provided at a second end of the second group of pipes.
  • coolant or heating fluid flows in via the inlet into the first group of conduits in a first direction, it can be deflected through the fluid connection, for example by approximately 90 ° and then in turn flow through 90 ° into the second group of conduits.
  • the heating medium and the coolant then flow out via the outlet from the second group of pipelines. Due to the double deflection in the fluid connection by 90 ° degrees, the heating medium or the coolant flows through the first group of pipes and the second group of pipes in opposite directions.
  • the working medium may also be heated by means of electromagnetic radiation.
  • sunlight can be used for heating the working medium.
  • gaseous and ORC media come into consideration.
  • a heat engine can be created, which is easy to operate with the help of sunlight and requires no other heat.
  • an external heater for providing a heating means.
  • a thermal oil could be heated by solar radiation and then fed to a heat exchanger.
  • a coolant of such a self-sufficient system would possibly be the ambient air or cooling water, as it may be available through lakes or streams, into consideration.
  • the heat engine further comprises a displacer which is movably arranged between the cold area and the hot area.
  • the displacer piston is formed of a thermally insulating material, so that the displacer does not allow little or no heat transfer from the hot to the cold region.
  • the displacer may include plastic or wood.
  • the Displacement piston made of polytetrafluoroethylene (PTFE), better known under the brand name Teflon® , or at least coated with Teflon® . In this way, the displacer on a high temperature resistance and excellent sliding properties.
  • the displacer is typically designed so that it almost completely fills the gap in the heat exchanger.
  • the displacer piston may have a comb-like structure extending between the heating medium and coolant tubes. Furthermore, a cushioning can be provided for the displacer. According to one embodiment, the displacement piston can be driven externally. For example, the displacer can be moved between the hot and cold areas via an electric, hydraulic or pneumatic drive.
  • the displacer piston described above allows the working fluid to be forced out of the hot or cold region of a given volume. Furthermore, the displacer is typically designed so that it fills the entire available between the heat exchanger volume of the hot or cold area. In this way, only the part of a respective volume is available to the working medium, in which the displacer is not located.
  • the displacer piston has a thermally insulating region that is configured to thermally isolate the hot region from the cold region.
  • the thermally insulating region of the displacer piston is made of a thermally insulating material, for example a plastic and / or a wood.
  • the displacer piston further comprises a heat accumulator, which is designed so that it is in a respective end position of the displacer in contact with the tubes of the heat exchanger.
  • the heat accumulator can comprise plates of heat-storing material, for example metal plates and in particular copper plates. Due to the heat storage of the displacer can act as a regenerator and thus increase the efficiency of the heat engine.
  • a fluid connection between the hot region and the cold region of the first and the second volume may be provided in the heat engine.
  • the working medium can be brought from the hot area into the cold area or vice versa.
  • the hot area and the cold area of each volume are at the same pressure level. In this way, no work against the gas pressure must be spent when moving the displacer. Only the bearings and friction forces of the piston and the relatively low flow dynamic losses in the working fluid must be expended for the shift.
  • the working medium can be brought from the hot area to the cold area and vice versa with little effort, so that the alternating heating and cooling in the respective volume can be realized.
  • the heat engine may further include at least one regenerator disposed in the fluid line. If the regenerator flows through the hot working medium, it absorbs part of the heat energy and stores it. In a later power stroke of the heat engine, the now cooled working fluid is moved over the regenerator in the hot area for heating. The cold working medium already absorbs heat from the regenerator so that it reaches the hot area already preheated. In this way, the regenerator can serve to increase the efficiency.
  • the regenerator may be formed in a housing wall of the first and / or the second volume. In particular, the regenerator may be connected upstream of an inlet or outlet for the working medium into the first and / or the second volume. In this way, a very compact design is achieved.
  • the first volume and / or the second volume may be cylindrical or cigar-shaped.
  • the ratio of surface to volume low, so that the thermal insulation of the volume is facilitated. Furthermore, this also leads to a reduction of the required material.
  • the first volume and / or the second volume are formed significantly smaller in at least one dimension than in the other two dimensions.
  • the first volume and the second volume may be provided as very flat elements.
  • the heat engine for example, on the underbody of motor vehicles, especially trucks mounted.
  • As a coolant in this case for example, serve air in the form of the wind, where as Heating means the exhaust gas of the engine is used.
  • Heating means the exhaust gas of the engine is used.
  • suitable choice of material such a heat engine can be relatively easily built.
  • An auxiliary motor can be driven by this heat engine, so that fuel savings of about 12% can be achieved.
  • the fluid conduit may be further configured to provide fluid communication between the hot region of the first volume and / or the second volume and a high pressure side of the work machine.
  • the fluid conduit may be further configured to provide fluid communication between the cold region of the first volume and / or the second volume and a low pressure side of the work machine.
  • the working machine is a motor.
  • the working machine can be designed as a pressure-operated rotary piston engine.
  • the machine is an electric generator.
  • the generator may be a pressure-operated electric generator according to the rotary piston principle.
  • the machine may be a pneumatic or hydraulic machine, wherein the pressure provided by the flowing working fluid is used to operate the pneumatic or hydraulic machine.
  • the pressure operated machine may be a pump or a chiller.
  • the machine may be a compressed air powered construction machine, in particular a jackhammer.
  • a heat exchanger can additionally be provided in the fluid line.
  • the heat exchanger can be connected for example between a regenerator and the working machine.
  • an intermediate heating of the working fluid in the fluid line can be done.
  • the intercooler, the cooling water of a motor can be passed through the heat exchanger.
  • a Walkerstoffzutechnisch and a coolant supply line be movable so that they are alternately connected to the first volume and the second volume can be.
  • the Schuffenzutechnisch and the coolant supply line may be rotatably mounted about a common axis, so that they can be brought in fluid communication with the first volume and the second volume alternately.
  • the machine which can be operated with the pressure of the working medium can be arranged on the common central axis of the first volume and of the second volume.
  • the machine operable with the pressure of the working medium may have a piston displaceable between a high-pressure side and a low-pressure side of the machine.
  • a method of operating a heat engine as described above.
  • This method comprises the steps of heating a working fluid in a first volume, pressurizing a machine operable with the working fluid with the heated working fluid, wherein the working fluid relaxes and performs work, introducing the relaxed working fluid into a second volume, cooling the working fluid in the second volume, heating the working fluid in the second volume, pressurizing the working fluid driven machine with the heated working fluid, the working fluid relaxing and performing work, introducing the relaxed working fluid into the first volume, and finally cooling the fluid Working medium in the first volume.
  • This method is thus characterized in that a working medium is heated in a volume, whereas it is cooled in a second volume at the same time.
  • the pressure generator can also be operated in such a way that a phase transition occurs during cooling and heating of the working medium.
  • an ORC medium or water can be used.
  • the gas or vapor phase ORC medium is liquefied on cooling.
  • a dramatic reduction in volume of the working medium occurs, so that a negative pressure is practically generated in the cooled volume.
  • the working medium flowing out of the hot volume condenses on entry into the cold region, so that substantially no pressure equalization is produced between the first and the second volume.
  • the liquid working fluid is evaporated on heating, whereby the volume multiplies or the pressure increases considerably.
  • the working medium in the first step of the method, is heated in a hot region of the first volume.
  • the working medium is admitted in a cold region of the second volume, in which it is then cooled.
  • the cooled working medium can furthermore be displaced into a hot region of the second volume, in which it is then heated.
  • the working medium heated in the hot region of the second volume may be admitted into a cold region of the first volume where it is cooled.
  • the cooled working medium can be displaced from the cold region into a hot region of the first volume. In this hot region of the first volume, the working medium is then reheated.
  • the method further comprises selectively supplying a heating means into the hot region of the first or second volume when the working medium is heated therein.
  • the method may further include selectively supplying a coolant into the cold region of the first or second volume when the working fluid therein is cooled. In this way, the heating means or the coolant is introduced only in the hot or the cold region of a respective volume, if the working medium in this volume is located. The heating medium flow or the coolant flow can be used particularly efficiently in this way.
  • the process described above can be carried out with any gaseous working media.
  • the process can be carried out with the working medium helium, wherein process temperatures in the range of several hundred degrees Celsius and process pressures in the range of several hundred bar can be driven.
  • the method can also be realized with an ORC medium.
  • the ORC medium used can be adapted to the available temperatures of the respective heating or coolant flows.
  • the medium can be moved from the cold side of a volume to the hot side of a volume or vice versa, without having to do work against a pressure.
  • a higher efficiency than in conventional ORC systems can be achieved because in these constantly the injection pump must be operated whereas in the heat engine according to the embodiments of the present invention, only the displacer needs to be moved without pressure.
  • a system comprises a first heat engine described above and at least one second heat engine or apparatus described above, wherein the heating means port of the second apparatus is connected to a heating means outlet of the first apparatus.
  • the first device is set up for a high-temperature process.
  • the first device can be set up for Schuffeneingangstemperaturen in the range of about 400 0 C to about 900 ° C.
  • the first device may be configured for heater output temperatures in the range of about 200 ° C to about 400 ° C. In this way, high temperature differences .DELTA.T can be used in the device.
  • the first device can be operated with a gas, wherein the gas is, for example, helium or nitrogen.
  • the second device may be configured for a process that has a lower process temperature compared to the first device.
  • the first device may be set up instead of a high-temperature process for such a medium-temperature process.
  • the second device or the first device for Schuffeneingangstemperaturen in the range of about 200 ° C to about 350 ° C be set up.
  • the second device or the first device for Schuffenausgangstemperaturen in the range of about 100 0 C to about 200 ° C is set up.
  • the thereby achievable temperature differences .DELTA.T can be used, for example, efficiently by the operation of the device with an ORC medium.
  • the second device or the first device is typically designed so that a phase transformation in the ORC medium is brought about.
  • other working media such as water, can be used.
  • the system further comprises a third device or a second device, wherein the heating medium connection of the third device or the second device is connected to a heating means of the second device or the first device and the third device or the second device is set up for a process which has a lower process temperature compared to the second device or to the first device.
  • the third device or the second device for Schuffeneingangstemperaturen in the range of about 80 ° C to about 200 0 C be set.
  • the third device or the second device for Schuffenausgangstemperaturen in the range of about 2O 0 C to about 100 0 C be set.
  • a low-temperature ORC medium can be used in this temperature range.
  • the third device or the second device is typically designed to effect a phase change in the low temperature ORC medium.
  • the cascaded systems described above use two, three, or more stages, each of which uses the waste heat still contained in the cooled heating means leaving one stage in the next stage.
  • the different stages are coordinated so that the respective subsequent stage is adapted by their process forth to the temperature of the emerging from the previous stage heating medium.
  • the working media are coordinated with each other.
  • the amounts, volumes, geometries and / or the construction of the respective stages can be adapted to the respective process temperatures of a stage.
  • the types and working media can differ between different levels.
  • a respective device in a cascaded system, may comprise a motor as a machine, wherein the respective motors are adapted to drive the same shaft. In this way, all motors contribute to the drive.
  • the respective devices may be connected to the same machine. In this construction, it is therefore not necessary to provide multiple machines but only a fluid connection of a respective device with the machine must be provided.
  • the system can be set up so that the first and the second device and optionally the third device can be operated out of phase with one another. In this way, the first and the second device and, if appropriate, the third device can be located at different times of the process at a given point in time. It can therefore be delivered to the machine constantly sent to each other with clever offset of the clocks of the respective devices pressure.
  • the system may comprise a first device described above and at least one second device described above, wherein the heating medium connection of the first device and the heating medium connection of the second device are connected to the same heating medium line. Furthermore, the system is set up so that the first and the second device can be operated out of phase with each other, so that the first device and the second device are in different cycles. According to a development, in each case the first device and the second device can have a motor as a machine and wherein the respective motors are set up so that they drive the same shaft. However, the first device and the second device may also be connected to the same machine. In such a system both devices run side by side at the same stage, ie the heating means has the same inlet temperature in both devices.
  • each of the previously described cascaded systems at each stage may have multiple devices connected in parallel.
  • the number of devices connected in parallel may be the same or different from stage to stage of the cascaded system.
  • a system which comprises an internal combustion engine, in particular a motor, and a device or a system described above or a system described above.
  • the heating medium connection of the device is connected to an exhaust gas outlet of the internal combustion engine.
  • the device may be equipped with a heating means, e.g. a thermal oil, are operated, in which case heat is removed from the exhaust gas by means of a heat exchanger and transferred to the heating medium.
  • a heat exchanger connected to the fluid line can furthermore be provided. This heat exchanger can be connected to a coolant line for heated coolant of the internal combustion engine, in particular of cooling water. In this way, the engine cooling water can be used for intermediate heating of the working medium.
  • the engine may be a diesel engine of a combined heat and power plant.
  • the diesel engine drives an electric generator and generates electricity.
  • the exhaust gas emitted by the diesel engine is supplied as a heating medium to a cascaded system, where it enters the first stage at about 450 ° C. There, the engine exhaust heat is removed to operate the device (s) of the first stage, so that the exhaust gas leaves the first stage of the system at about 250 ° C.
  • a pure gas process can be run with helium or nitrogen as the working medium.
  • the exhaust gas now enters a second stage of the system at approximately 250 ° C.
  • the engine exhaust already cooled in the first stage, further heat to operate the device (s) of the second stage is withdrawn, so that the exhaust gas leaves with about 12O 0 C, the second stage of the system.
  • a high-temperature ORC process can be run.
  • High-temperature ORC media which are still chemically stable at the process temperatures in the range of 200 ° C. may be used as the working medium.
  • the high temperature ORC process can now be followed by a third stage in which a low temperature ORC process is run.
  • the cooled in the first and second stage exhaust gas now enters with about 12O 0 C in the third stage, where it is deprived of heat and it leaves the third stage with about 7O 0 C.
  • This low-temperature ORC Process can be with a low-temperature ORC medium, which evaporates, for example, already at about 2O 0 C to 5O 0 C, operated.
  • a heat exchanger in this third stage may be provided from the hot about 9O 0 C engine cooling water flows through.
  • regenerators can be used in all or in individual stages, store the heat and serve to preheat the cooled working medium.
  • a method for utilizing waste heat comprises the steps of providing a device as described above, each of which alternately heating or cooling the working medium in the first and in the second volume, so that the working medium in the first volume and the working medium in the second volume having a pressure difference, connecting the first volume and the second volume via the fluid line and operating a machine connected to the fluid line with the pressure difference.
  • a map used for heating the working medium heating means may in one exemplary embodiment having an inlet temperature in the range of about 400 0 C to about 900 0 C. Further, after heating the working medium, the heating means may have a temperature in the range of about 200 ° C to about 400 ° C.
  • the working medium may be a gas or gas mixture, in particular helium and / or nitrogen.
  • a heating medium used to heat the working fluid may have an inlet temperature in the range of about 200 ° C to about 350 ° C.
  • the heating means may have a temperature in the range of 100 0 C to 200 0 C after heating the working medium.
  • the working medium may be, for example, an ORC medium or a vapor, wherein a phase transition of the working medium is typically caused during heating or cooling of the working medium.
  • a method used for heating the working medium heating means comprises an inlet temperature ranging from about 8O 0 C to about 200 0 C.
  • the heating means may have a temperature in the range of about 2O 0 C to about 100 0 C.
  • the working medium may be a low-temperature ORC medium, wherein upon heating or cooling of the working medium, a phase transition of the working medium is brought about.
  • cooled working fluid may be preheated in a heat exchanger.
  • a plurality of pressure generating devices may be operated with clock shifted from each other.
  • a heat engine includes a first unit having a first radiator K1 and a first evaporator B1, B2 connected to each other via a first fluid line F1, the first radiator K1 being located above the first evaporator B1, B2 and the first one Fluid line Fl can be shut off by means of a first valve Vl, a second unit with a second radiator K2 and a second evaporator B3, B4, which are connected to each other via a fourth fluid line F4, wherein the second radiator K2 is disposed above the second evaporator B3, B4 and the fourth fluid line F4 can be shut off by means of a second valve V2, and a machine M which can be operated with a pressurized fluid, the machine being connected to the first evaporator Bl via a second fluid line F2 and to the first radiator Kl and via a third fluid line F3 via a fifth fluid line F5 with the second evaporator B3 and via a sech Ste fluid line F6 is connected to the second radiator K2.
  • a method of operating such a heat engine comprises heating a liquid in an evaporator so that the liquid evaporates, operating a machine with the evaporated liquid, condensing the evaporated liquid in a cooler, and returning the condensed liquid to the evaporator, wherein the cooler is arranged above the evaporator, so that the condensed liquid flows back into the evaporator due to the gravitational force.
  • a method of operating such a heat engine comprises heating a liquid in a first evaporator and in a second evaporator so that the liquid evaporates, operating a machine with the evaporated liquid, condensing the evaporated liquid in a first cooler and in a second cooler, and returning the condensed liquid to the first evaporator and the second evaporator, wherein the first cooler above the first evaporator and the second cooler above the second evaporator is arranged so that the condensed liquid flows back due to the gravitational force in the first evaporator and in the second evaporator.
  • the first evaporator and the second evaporator can be clocked offset from one another, so that the machine is operated alternately with vaporized liquid from the first evaporator and from the second evaporator.
  • the vaporized liquid may be passed from the first evaporator into the first cooler and the vaporized liquid from the second evaporator into the second cooler.
  • the vaporized liquid may be passed from the first evaporator into the second cooler and the vaporized liquid from the second evaporator into the first cooler.
  • Fig. 1 is a schematic representation of a heat engine according to an embodiment of the present invention.
  • Fig. 2 is a plan view of an embodiment of a first or second volume in a heat engine.
  • Fig. 3 is a cross-sectional view of the arrangement shown in Fig. 2 along the line A-A.
  • Fig. 4 is a cross-sectional view of the arrangement shown in Fig. 2 along the line B-B.
  • Fig. 5 is a cross-sectional view of the arrangement shown in Fig. 2 along the line C-C.
  • Fig. 6 shows a heat engine according to an embodiment of the present invention in a first state.
  • FIG. 7 the heat engine of FIG. 6 in a second state.
  • FIG. 8 the heat engine of FIG. 6 in a third state.
  • FIG. 9 the heat engine of FIG. 6 in a fourth state.
  • FIG. 10 the heat engine of FIG. 6 in a fifth state.
  • FIG. 12 the heat engine of FIG. 6 in a seventh state.
  • Fig. 13 the heat engine of FIG. 6 in an eighth state.
  • Fig. 14 shows another embodiment of the heat engine.
  • Fig. 15 is a cross-sectional view of yet another embodiment of a volume.
  • FIG. 16 shows a cross section through the volume according to FIG. 15 along the line A-A.
  • 17 is a plan view of an embodiment of a first or second volume in a heat engine.
  • FIG. 18 shows a heat engine according to an embodiment of the present invention in a first state.
  • FIG. 19 the heat engine of FIG. 18 in a second state.
  • FIG. 20 the heat engine of FIG. 18 in a third state.
  • FIG. 21 the heat engine of FIG. 18 in a fourth state.
  • FIG. 23 shows the heat engine according to FIG. 18 in a sixth state.
  • FIG. 24 the heat engine of FIG. 18 in a seventh state.
  • FIG. 25 shows the heat engine according to FIG. 18 in an eighth state.
  • Fig. 26 shows another embodiment of the heat engine.
  • Fig. 27 is a cross-sectional view of yet another embodiment of a heat engine.
  • FIG. 28 shows a cross section through the volume of FIG. 12 along the line A-A.
  • Fig. 29 is a schematic representation of a device according to another embodiment of the present invention.
  • Fig. 30 is a schematic representation of a system according to an embodiment of the present invention.
  • Fig. 31 is a schematic diagram of another system according to an embodiment of the present invention.
  • Fig. 32 is a schematic representation of still another system according to an embodiment of the present invention.
  • Fig. 33 is a schematic representation of yet another system according to an embodiment of the present invention.
  • Fig. 34 is a schematic diagram of a system according to another embodiment of the present invention.
  • Fig. 35 shows a system with an internal combustion engine according to another embodiment of the invention.
  • Fig. 36 is a cross-sectional view of an electric generator as may be used in an embodiment of the present invention.
  • Fig. 37 is a cross-sectional view of a rotary piston engine as may be used in another embodiment of the present invention.
  • Fig. 38 is a schematic representation of an arrangement with two series-connected motors.
  • Fig. 39 is a schematic representation of a heat engine according to another embodiment of the present invention.
  • the heat engine 1000 comprises a first volume 100 and a second volume 200.
  • the first volume 100 and the second volume 200 each contain a working medium 10.
  • the working medium 10 is a fluid, for example a gas, a vapor such as water vapor or an ORC medium.
  • a gas for example, helium, nitrogen or air or any suitable gas mixtures can be used as a gaseous working medium.
  • ORC media both high temperature and low temperature ORC media can be used.
  • the first volume 100 and the second volume 200 are connected to one another via a fluid line 400. Between the first volume 100 and the second volume 200, a machine 300 operable with the working medium 10 is arranged.
  • a quantity of heat Q can be supplied to the first volume 100 and a heat quantity Q can be taken from the second volume 200 (arrows in FIG. 1). Furthermore, it is indicated by the dashed arrows in FIG. 1 that, conversely, a quantity of heat Q is withdrawn from the first volume 100 and a quantity of heat Q can be supplied to the second volume 200.
  • 300 mechanical work W can be performed by the machine.
  • the working principle of the heat engine 1000 will be explained below.
  • the first volume 100 and the second volume 200 are initially held in a separate state.
  • the working medium 10 in the first volume 100 is heated by supplying a quantity of heat Q.
  • the pressure in the first volume 100 increases.
  • the working medium 10 located in the second volume 200 is cooled by discharging a quantity of heat Q.
  • the pressure in the second volume 200 decreases.
  • the two volumes are connected to one another via the fluid line 400 and thus a pressure equalization between the first volume 100 and the second volume 200 allowed.
  • the working medium 10 in the first volume 100 will flow into the second volume 200 via the fluid line 400 due to its higher pressure.
  • the flowing working medium 10 thereby performs mechanical work on the machine 300.
  • the machine 300 can be designed as a pressure-operable machine and / or as a turbomachine, for example a turbine.
  • heat is now supplied to the second volume, as indicated by the dashed arrow.
  • the working medium 10 present in the first volume 100 is now cooled by removing a quantity of heat Q.
  • the heated working medium is then present in the second volume 200 under high pressure, while the working medium 10 is present in the first volume 100 under lower pressure.
  • a pressure equalization between the second volume 200 and the first volume 100 via the fluid line 400 take place.
  • the heated pressurized working fluid flows from the second volume 200 into the first volume 100, performing mechanical work W on the engine 300.
  • the pressure generator can also be operated in such a way that a phase transition occurs during cooling and heating of the working medium.
  • an ORC medium or water can be used.
  • the gas or vapor phase ORC medium is liquefied on cooling.
  • a dramatic reduction in volume of the working medium occurs, so that a negative pressure is practically generated in the cooled volume.
  • the working medium flowing out of the hot volume condenses on entry into the cold region, so that substantially no pressure equalization is produced between the first and the second volume.
  • the liquid working fluid is evaporated on heating, whereby the volume multiplies or the pressure increases considerably.
  • FIG. 2 shows a plan view of the first volume 100
  • FIG. 3 shows a cross-sectional view through the first volume 100 along the line AA in FIG. 2
  • FIG. 4 shows a cross-sectional view of the first volume 100 along the line BB in FIG. 2
  • FIG. 5 shows a cross-sectional view through the first volume 100 along the line CC in FIG. 2.
  • the first volume 100 has a cold area 110 and a hot area 120.
  • coolant tubes 112 are arranged, which extend substantially parallel to the longitudinal axis of the first volume 100.
  • the coolant tubes 112 are connected via a coolant inflow 114 to a coolant line (not shown).
  • Coolant 20 can be introduced into the coolant tubes 112 via the coolant line and the coolant inflow 114.
  • a chamber 140 for the working medium 10 is arranged between the coolant tubes 112.
  • the chamber 140 has a port 142, can be admitted through the working medium 10 in the chamber 140 or omitted.
  • the Schuschröhren have a Bankofsky 124 through which a heating means 30 can be inserted into the Bankschröhren 122. Furthermore, a chamber 150 is formed between the Schuschröhren 122, which has a connection 152. Working medium can be introduced into the chamber 150 via the connection 152. In the illustrated volume 100, the area 140 between the coolant tubes and the area 150 between the heating medium tubes form a single continuous chamber.
  • a displacer 160 is arranged in this chamber.
  • the displacer 160 can be moved between the cold region 110 and the hot region 120.
  • the displacer can be driven externally, for example by an electric drive, a pneumatic or a hydraulic drive.
  • the displacer piston is made of a thermally insulating material, such as a plastic and / or a wood.
  • the displacer 160 can be made of Teflon® or have a Teflon® coated surface.
  • the material properties of Teflon ® are favorable for the present application in that Teflon ® has a heat resistance and excellent sliding properties. According to the exemplary embodiment shown in FIG.
  • the displacement piston 160 is dimensioned in its longitudinal extension such that it extends into the region of the thermal insulation 130 in a respective end position. Since the displacement piston 160 is thermally insulating, in this way a heat transfer from the hot region 120 into the cold region 110 of the volume 100 is suppressed. Furthermore, the spatial structure of the displacer 160 is formed so that it completely fills the entire volume of the respective chamber 140 in the cold region and the chamber 150 in the hot region. In particular, the displacement piston 160 may have a comb-like structure extending between the coolant tubes 112 and the heating medium tubes 122. According to one embodiment, a cushioning (not shown) for the displacer 160 is provided so that the displacer slides smoothly when moving in the respective end position.
  • the displacement piston 160 in its end position shown, ensures that the working medium 10 has been substantially completely displaced from the hot region 120. Only in the connection region 150 of the hot region 120 is still a small remainder of the working medium contained. On the other hand, the chamber 140 is completely available for cooling in the cold region 110 of the working medium 10. Now, if the displacer 160 moved into its final position in the cold area 110, he would push out the working fluid from the cold area 110. At the same time, working medium could then flow into the volume released by the displacer 160 in the hot region 120. In this way, by displacing the displacement piston 160, only the cold region 110 or the hot region 120 for the working medium can be made accessible in the volume 100.
  • the sectional view shown in FIG. 4 along the section line B-B clearly shows the comb-like structure of the displacement piston 160.
  • an intermediate space between the heating medium tubes 122 is created by the side walls 102 and the cover 104 of the volume 100.
  • the geometric shape of the displacer 160 is chosen so that it completely fills this gap. For this he has a substantially comb-like structure.
  • the wall thickness of the side walls 102 and the cover 104 can be adapted to the process pressures.
  • the cross-section along the section line C-C shown in FIG. 5 also shows the comb-like chamber volume 140 formed between the side walls 102 and the cover 104 of the volume 110.
  • the working medium 10 located therein can undergo intensive heat exchange with the coolant 10 located in the coolant tube 112.
  • a large surface for the heat exchange is provided by the comb-like structure of the coolant tubes or Schuffenrohre.
  • FIG. 6 shows an exemplary embodiment of a heat engine whose detailed mode of operation will then be explained in FIGS. 7 to 13.
  • the heat engine in this case comprises a first volume 100 and a second volume 200.
  • the first volume 100 and the second volume 200 are in accordance with the in Figs. 2 to 5 described embodiments constructed. Furthermore, in this embodiment, the first volume 100 and the second volume 200 are constructed identically, but this is not essential to the practice of the present invention.
  • the cold region 110 of the first volume 100 and the cold region 210 of the second volume 200 can be supplied with coolant 20 via coolant inflows 114, 214 become. In this case, for example, the cold region 110 of the first volume 100 and the cold region 210 of the second volume 200 can be supplied via a common coolant line 116.
  • a switch 170 is installed, which can selectively direct the coolant flow in the first volume 100 or the second volume 200.
  • the first volume 100 has a coolant outflow 118 and the second volume 200 has a coolant outflow 218.
  • the coolant outflow 118 and the coolant outflow 218 can lead into a common cooling line.
  • the coolant may optionally be provided to the cold region 110 of the first volume 100 or the cold region 210 of the second volume 200.
  • a heating means 30 may be provided via a heating line 126.
  • a switch 180 is inserted into the heating medium line 126, which can initiate the heating means either via the port 124 in the Schuffenrohre 122 of the first volume 100 or via the port 224 in the Schuffenrohre 222 of the second volume 200. Also provided are heating medium outflows 128 from the first volume and 228 from the second volume, wherein the heating agent outflows 128 and 228 may flow into a common heating medium drainage.
  • the fluid line 400 shown so far only schematically is shown in more detail in this example, in particular a possible valve arrangement is shown.
  • FIGS. 6 to 13 is merely intended to show the basic fluid-technical control options, but this does not represent a detailed fluid-technical circuit diagram. In the practical implementation of such a heat engine, it can therefore obviously come to significant deviations of the valve arrangements shown here.
  • the fluidic circuitry of the embodiment shown in FIG. 6 is substantially symmetrical between the upper and lower halves of the illustration. Therefore, the fluidic shading of the first volume 100 will first be described below. In this case, a valve 410 is connected behind the connection 142 of the cold region 110.
  • Valve 410 is configured to control emptying or discharging of working medium 10 from chamber 140.
  • the port 142 of the cold section 110 is connected to a low-pressure side 320 of the work machine 300 via the valve 410 and via a control valve 420 and another valve 430.
  • the control valve 420 has four inputs or outputs wherein it is arranged to establish a fluid connection between respective inlets and outlets.
  • the further valve 430 may serve to block the connection from the low pressure side 320 of the engine 300 to the control valve 420.
  • the fluid line furthermore has a line which can be connected from the connection 152 of the hot region 120 of the first volume 100 to a high-pressure side 310 of the work machine 300.
  • connection can be made via the control valve 420 and another check valve 440. If the check valves 430 and 440 are switched to passage, via the control valve 420, a fluid connection between the connection 142 of the cold area 110 and the low pressure side 320 of the machine 300 and the port 152 of the hot area 120 and the high pressure side 310 of the machine 300th getting produced.
  • the connection of the cold area 220 can be shut off by means of a valve 415.
  • the cold region 210 can be connected via a further shut-off valve 435 to the low-pressure side 320 of the machine 300.
  • a connection 252 of the hot region 220 can be connected via the control valve 425 and a check valve 445 to the high-pressure side 310 of the work machine 300.
  • the valves 410 and 415 and the control valves 420 and 425 respectively allow fluid communication between the hot areas 120, 220 and the cold areas 110, 210 of the first volume 100 and the second volume 200, respectively.
  • regenerators 146, 246 are connected in the fluid lines, the function of which will be explained later. It should, however, be pointed out that the regenerators 146, 246 can also be installed in a housing wall of the first volume 100 and the second volume 200, respectively.
  • the working medium 10 located in the chamber 140 of the cold area 110 is cooled.
  • coolant 20 is introduced into the coolant tubes 112 of the first volume via the fluid line 116, the switch 170 and the port 114.
  • the valve 410 blocks the chamber 140 and the displacer 160 is disposed in the hot region 120 of the first volume.
  • This working medium is also locked in the volume, since the valve 420 is blocking with respect to the voltage applied to the connection of the hot region 120 line.
  • the working medium contained in the chamber 140 now gives off some of its heat to the coolant flowing through the cooling tubes 112. Due to the constant volume of the chamber 140 and the constant mass of the working medium 10 in this chamber 140 pressure and temperature of the working medium 10 fall. If a process is carried out with phase transformation of the working medium, the possibly still gaseous portions of the working medium, such as an ORC -Mediums, liquefied.
  • the displacement piston 260 is arranged in its end position in the cold region 210.
  • the working medium 10 is located in the chamber 250 in the hot region 220 of the second volume 200.
  • a heating medium 30 is provided in the heating medium tubes 222 via a heating medium line 126, the point 180 and the heating medium inlet 224.
  • the working medium 10 then absorbs heat from the heating means 30 in the hot region 220. Since the volume of the chamber 250 remains unchanged, pressure and temperature of the heating medium 10 rise in the hot region 220. In particular, in a process with phase transformation of the working medium, a strong increase in pressure can take place when the liquid working medium evaporates. At the end of this first step, therefore, there are cold working medium under relatively low pressure in the cold region 110 of the first volume 100 and hot working medium in the hot region 220 of the second volume 200 under high pressure.
  • FIG. 7 now shows a next state of the heat engine according to FIG. 6.
  • the valve 445 which is still blocking in FIG. 6 has been turned on, so that a fluid connection with the high-pressure side 310 of the work machine 300 is established between the connection 252 of the hot region 220 .
  • the valve 410 is turned on, so that between the low pressure side 320 of the machine 300 via the valve 430 and the control valve 420, a fluid connection with the terminal 142 of the cold region 110 of the first volume 100 is made.
  • a fluid connection is thus established between the hot region 220 of the second volume 200 and the cold region 110 of the first volume 100.
  • the hot working medium 10 Due to the pressure difference, the hot working medium 10 now flows from the hot area 220 into the cold area 110. In doing so, the flowing medium on the machine 300 performs mechanical work that can be removed in this way.
  • FIG. 8 now shows a state of the heat engine following the state shown in FIG. 7.
  • the control valve 420 is switched so that a fluid connection is established between the connection 142 of the cold region 110 and the connection 152 of the hot region 120.
  • the control valve 425 is switched so that between the hot area 220 and the cold area 210 a fluid connection is made. It should be noted that in this way also a possibly existing pressure difference between the hot area 120 and the cold area 110 of the first volume 100 and the hot area 220 and the cold area 210 of the second volume 200 is compensated, so that the respective hot and cold regions of the first volume 100 and the second volume 200 have the same pressure level.
  • Fig. 9 now shows the next step in the operation of the heat engine.
  • the displacement piston 160 is moved from the hot side 120 to the cold side 110.
  • the working medium previously located in the cold region 110 is thereby displaced via the established fluid connection into the hot region 120 of the first volume. Since the cold region 110 and the hot region 120 have no pressure difference, the displacer 160 does not have to work against pressure. The method of the displacer 160 thus requires only a small amount of energy to overcome bearing and frictional forces.
  • the displacement piston 260 is now moved from the cold region 210 into the hot region 220.
  • the pressure equalization between the hot area 220 and the cold area 210 no pressure work to be done.
  • the working medium 10 is thereby displaced from the hot region 220 into the cold region 210.
  • the fluid connection between the hot region 120 and the cold region 110 or between the cold region 210 and the hot region 220 is now blocked so that the working media in the chamber 150 of the hot Area 120 and the chamber 240 of the cold area 210 are locked.
  • the switch 170 is now switched so that the coolant 20 is introduced via the connection 214 into the coolant tubes 212 of the cold region 210.
  • the switch 180 is switched, so that the heating means 30 is now introduced via the port 124 in the Schuffenrohre 122 of the hot region 120.
  • the working medium is now heated in the first volume, namely in the hot region 120, and cooled in the second volume, namely in the cold region 210.
  • the port 152 of the first volume hot region 120 is connected to the high pressure input 310 of the engine 300.
  • the port 242 of the cold region 210 is connected to the low pressure side 320 of the engine.
  • the working medium Due to the pressure difference between the high-pressure working medium in the hot region 120 and the low-pressure working medium in the cold region 210, the working medium flows from the hot region 120 into the cold region 210 until the pressure difference is equalized. In this case, the flowing working medium performs mechanical work on the machine 300, which can be removed there.
  • control valves 420 and 425 are set analogously to FIG. 8 such that between the hot region 120 and the cold region 110 of the first volume and the cold region 210 and the hot region 220 of FIG second volume, a fluid connection and thus a pressure equalization is produced.
  • the displacement piston 160 is now displaced again from the cold region 110 of the first volume into the hot region 120.
  • the displacer 260 is displaced from the hot region 220 into the cold region 210.
  • the coolant diverter 170 and the heating means 180 are switched so that coolant is supplied to the cold zone 110 of the first volume and heating means is supplied to the hot zone 220 of the second volume.
  • the working medium 10 in the cold region 110 of the first volume 100 is therefore now cooled and heated the working fluid in the hot region 220 of the second volume.
  • the heat engine is now in the initial state shown in FIG. 6, so that the process can be performed again.
  • the regenerator 146 is cooled again.
  • the regenerator 240 flows through, thereby absorbing and storing heat. If, in the step shown in FIG. 13, the cooled working medium is displaced from the cold region 210 into the hot region 220, it absorbs heat stored by the regenerator 246 there, cools it and reaches the hot region 220 preheated.
  • Fig. 14 shows another embodiment of the present invention.
  • further heat exchangers 148, 248 are provided.
  • These heat exchangers 148, 248 are flowed through by a heating medium, which typically has a lower temperature than the heating means in the hot regions 120, 220.
  • the heating medium in the heat exchanger can be flowed through by cooling water of an engine.
  • the or the heat exchangers 148, 248 may be provided alternatively or in addition to the regenerators 146, 246. In one embodiment, both regenerators and heat exchangers are provided.
  • the cooled in the cold region 110 working medium while moving through the regenerator 146 may be brought to a temperature of, for example 6O 0 C.
  • the additional heat exchanger 148 flows through the heating means, for example cooling water, approximately has a temperature in the range of 9O 0 C. If now the at 6O 0 C heated working medium additionally guided via the heat exchanger 148, a pre-heating the working medium prior to entering the hot region 120 to about 8O 0 C can be achieved. In this way, on the one hand, further heat can be withdrawn from the cooling water and, on the other hand, the working medium can already be preheated. In this way, the efficiency of an overall process can be significantly increased. It should also be pointed out that the above-mentioned numerical examples are only to be understood as examples and, in particular, do not imply any definition of specific temperature and / or pressure ranges and / or working media.
  • a switch (not shown) can also be provided here, which alternately provides the second heating means to one of the heat exchangers 148, 248 when it is needed there.
  • Fig. 15 shows a cross-sectional view of still another embodiment of a volume 100 having a cigar shape.
  • the heat exchangers each comprise a first group 112 A, 122 A of pipelines and a second group 112B, 122B of pipelines.
  • the first and the second group of pipelines are each connected to one another via a fluid connection 144, 154.
  • the pipelines are arranged within the volume 100 so that they are flowed through in opposite directions by the heating medium or the coolant.
  • first group 112A, 122A of tubing and the second group 112B, 122B of tubing together with the fluidic connection 144, 154 are substantially U-shaped.
  • a coolant or heating means inlet 114, 124 is provided at one end of the first group 112 A, 122 A of the pipelines.
  • a coolant or heating means outlet 118, 128 may be provided at a second end of the second group 112B, 122B of piping.
  • coolant or heating means via the inlet 114, 124 flows into the first group 112 A, 122 A of pipes in a first direction, it can be deflected through the fluid connection 144, 154 by about 180 ° and then in turn into the second group 112B, 122B of pipes.
  • the heating medium and the coolant then flow out of the second group of pipes via the outlet 118, 128. Due to the deflection in the fluid connection, the heating medium or the coolant flows through the first group 112 A, 122 A of pipelines and the second group 112 B, 122 B of pipelines in mutually opposite directions.
  • the surface available for the heat transfer can be increased and, on the other hand, the time in which the heating medium or the coolant flows through the heat exchanger can be extended. In this way, the heat exchange is more efficient and the efficiency of the heat engine is improved.
  • the fluid connection 144, 154 is formed via a movably inserted part 143, 153.
  • the movable part 143, 153 can move relative to the outer shell of the volume 100 and thus adapt to a change in length of the tubes 112 A, 112 B, 122 A, 122 B. Length changes of the tubes 112A, 112B, 122A, 122B may occur due to heating or cooling of the tubes.
  • FIG. 16 shows a cross section through the volume according to FIG. 15 along the line AA.
  • the heat exchanger each has a plurality of substantially parallel tubes 112 A, 112B for the coolant.
  • the surface available for heat exchange in the heat exchanger is increased.
  • a plurality of relatively small diameter tubes are arranged side by side and connected to each other, for example by welding.
  • a similar structure may be realized by providing a single larger rectangular profile into which partitions are inserted. The advantage of such an arrangement is that, due to the relatively small individual cross sections, the tubes are pressure-resistant relative to the ambient pressures that occur, in particular, when the working medium is heated.
  • the heat exchanger has a plurality of such tube bundles, which are spaced apart from each other.
  • the working medium can flow into the interstices 140 between the respective tube bundles and absorb heat there from a heating medium on the surface of the respective tube bundles or dissipate heat to a coolant.
  • the first volume 100 has a cold area 110 and a hot area 120.
  • coolant tubes 112 are arranged, which extend substantially parallel to the longitudinal axis of the first volume 100.
  • the coolant tubes 112 are connected to a coolant line (not shown) via a coolant inflow (not shown).
  • Coolant 20 can be introduced into the coolant tubes 112 via the coolant line and the coolant inflow.
  • a chamber 130 for the working medium 10 is arranged between the coolant tubes 112, a chamber 130 for the working medium 10 is arranged.
  • the chamber 130 has a port 132, can be admitted via the working medium 10 in the chamber 130 or omitted.
  • a displacer 140 is arranged in this chamber.
  • the displacer 140 can be moved between the cold region 110 and the hot region 120.
  • the displacer can be driven externally, for example by an electric drive, a pneumatic or a hydraulic drive.
  • the displacement piston 140 has a thermally insulating region 146, which is formed so that it thermally insulated the hot region 120 of the cold region 110.
  • the thermal insulating region 146 extends from sidewall to sidewall of the chamber 130 and also from the bottom to the ceiling of the chamber 130.
  • the thermally insulating region 146 forms a slidable wall which places the chamber 130 in a hot region 120 and in a cold region Division 110 shares.
  • the thermally insulating region of the displacer piston is made of a thermally insulating material, for example a plastic and / or a wood.
  • the thermally insulating region 146 may be made of Teflon® or have a Teflon® coated surface.
  • Teflon ® The material properties of Teflon ® are favorable for the present application in that Teflon ® has a heat resistance and excellent sliding properties. Since the displacement piston 140 is thermally insulating through the region 146, in this way a heat transfer from the hot region 120 into the cold region 110 of the volume 100 is suppressed.
  • the displacer 140 further comprises a heat accumulator 142, 144 which is formed according to the embodiment shown so that it is in a respective end position of the displacer 140 with the tubes 112, 122 of the heat exchanger in contact. In this way, a heat exchange between the heat storage 142, 144 and the heat exchanger is made possible.
  • the displacement piston 140 has a comb-like structure in which the heat accumulators 142 substantially completely fill the intermediate space between the heating medium tubes 122 in the end position of the displacer piston shown.
  • the heat accumulator comprises several pairs of plates of heat-storing material, for example metal plates and in particular copper plates. These plates are pressed against the tubes 122 and the common planar surface of the tubes.
  • the plates may have some mobility and a conical mandrel (not shown) may be provided.
  • a conical mandrel (not shown) may be provided.
  • the displacer moved into its final position, so the mandrel forces the plates apart, for example against a spring, so that they are pressed against the tubes 122.
  • the plates from the heating medium tubes 122 through which heating mediums 122 receive and store heat.
  • the displacement piston 140 is later moved into its opposite end position in the cold region 110, then the warmed plates 142 release their heat to a working medium to be heated, which is introduced into the hot region 120.
  • the plates 142 act as a regenerator. Furthermore, they use or store heat contained in the heating means even if no working medium is heated in the hot region 120.
  • the plates 144 facing the cold region release heat to the coolant tubes 112 and the coolant 20 flowing therein. In this way, the plates 144 are cooled. If hot working medium is now introduced into the cold region 110 for cooling, the plates 144 can absorb heat from the working medium and thus cool the working medium in addition to the cooling tubes 112. In this way, the plates 144 also act as regenerators.
  • the spatial structure of the displacer piston 140 is formed so that it substantially completely fills the entire volume of the chamber 130 in the hot region 120 and the chamber 130 in the cold region 110 when it is moved to its end position.
  • the displacement piston 140 may have the above-described comb-like structure extending between the coolant tubes 112 and the heating medium tubes 122.
  • the working medium 10 located in the chamber 130 can enter into an intensive heat exchange with the coolant 20 located in the coolant tube 112.
  • the comb-like structure of thehariteLrohre or Schuffenbachrohre a large surface for the heat exchange is provided.
  • a cushioning (not shown) is provided for the displacer piston 140, so that the displacer slides smoothly when moving in the respective end position.
  • a cushioning (not shown) is provided for the displacer piston 140, so that the displacer slides smoothly when moving in the respective end position.
  • metal plates are used as heat storage 142, 144, such end cushioning may be useful, since then the displacer 140 may have a significant inertial mass.
  • thermally insulating portion 146 of the displacer piston 140 in the illustrated end position ensures that the heating medium tube 122 with the heating means 30 therein is completely thermally insulated from the coolant tube 112 and the working medium 10 located in the cold region chamber 130 , If displacement piston 140 were then moved into its end position in the cold region, the region isolated 146, the coolant tube 112 and the coolant therein 20 from the then located in the hot area working fluid 10 and located in Walkerstoffbach 122 located heating means 30. In this way can be effected by moving the displacer 140 that in the volume 100 only in each case cold area 110 or the hot area 120 is accessible to the working medium.
  • Fig. 18 shows an exemplary embodiment of a heat engine or a pressure generator whose detailed operation with reference to FIGS. 19 to 25 will be explained.
  • the pressure generator comprises a first volume 100 and a second volume 200.
  • the first volume 100 and the second volume 200 are constructed in accordance with the embodiment described in FIG. Furthermore, in this embodiment, the first volume 100 and the second volume 200 are constructed identically, but this is not essential to the practice of the present invention.
  • the cold region 110 of the first volume 100 and the cold region 210 of the second volume 200 can be supplied with coolant 20 via coolant inflows 114, 214. In this case, for example, the cold region 110 of the first volume 100 and the cold region 210 of the second volume 200 can be supplied via a common coolant line 116.
  • a Y-piece is installed, which can direct the flow of coolant into the first volume 100 and the second volume 200.
  • the first volume 100 has a coolant outflow 118 and the second volume 200 has a coolant outflow 218.
  • the coolant outflow 118 and the coolant outflow 218 can lead into a common coolant line.
  • the coolant may be provided to the cold region 110 of the first volume 100 or the cold region 210 of the second volume 200.
  • a heating means 30 may be provided via a heating line 126.
  • a Y-piece is inserted into the Schuffentechnisch 126, which can initiate the heating means via the port 124 in the Schuffenrohre 122 of the first volume 100 and via the port 224 in the Schuffenrohre 222 of the second volume 200. Also provided are heating medium outflows 128 from the first volume and 228 from the second volume, wherein the heating agent outflows 128 and 228 may flow into a common heating medium drainage.
  • the fluid line 400 shown so far only schematically is shown in more detail in this example, in particular a possible valve arrangement is shown. It should be taken into account that the in Figs. 18 to 25 shown arrangement only to show the basic fluid power control options, but this is not a detailed fluid power circuit diagram. In the practical realization of such a pressure generator, it can therefore of course come to significant deviations of the valve arrangements shown here.
  • the fluidic circuitry of the embodiment shown in FIG. 18 is substantially symmetrical between the upper and lower halves of the illustration. Therefore, the fluidic shading of the first volume 100 will first be described below.
  • a valve 410 is connected behind the connection 132 of the cold region 110. The valve 410 is configured to control the admission or discharge of the working medium 10 from and into the chamber 130.
  • the port 132 of the cold region 110 is connected via the valve 410 and via a control valve 420 and another valve 430 to a low pressure side 320 of the work machine 300.
  • the control valve 420 has four inputs and outputs, wherein it is set up to establish a fluid connection between respective inputs and outputs.
  • the further valve 430 may serve to block the connection from the low pressure side 320 of the engine 300 to the control valve 420.
  • the fluid line furthermore has a line which can be connected from the connection 134 of the hot region 120 of the first volume 100 to a high-pressure side 310 of the work machine 300. In this case, the connection can be made via the control valve 420 and another check valve 440.
  • connection of the cold area 220 can be shut off by means of a valve 415.
  • the cold region 210 can be connected via a further shut-off valve 435 to the low-pressure side 320 of the machine 300.
  • regenerators 150, 250 are connected in the fluid lines, the function of which will be explained later. However, it should be pointed out be that the regenerators 150, 250 may be installed in a housing wall of the first volume 100 and the second volume 200.
  • the working medium 10 located in the chamber 130 of the cold area 110 is cooled.
  • coolant 20 is introduced into the coolant tubes 112 of the first volume via the fluid line 116 and the port 114.
  • the valve 410 shuts off the chamber 130 and the displacer 140 is located in the hot region 120 of the first volume.
  • This working medium is also locked in the volume, since the valve 420 is blocking with respect to the voltage applied to the connection of the hot region 120 line.
  • the working medium located in the chamber 130 now gives off part of its heat to the coolant flowing through the cooling tubes 112. Due to the constant volume of the chamber 130 and the constant mass of the working medium 10 in this chamber 130 pressure and temperature of the working medium 10 fall. If a process is carried out with phase transformation of the working medium, the possibly still gaseous portions of the working medium, such as an ORC -Mediums, liquefied.
  • the displacement piston 240 is arranged in its end position in the cold region 210.
  • the working medium 10 is located in the chamber 230 in the hot region 220 of the second volume 200.
  • a heating medium 30 is provided in the heating medium tubes 222 via a heating medium line 126 and the heating medium inlet 224.
  • the working medium 10 then absorbs heat from the heating means 30 in the hot region 220. Since the volume of the chamber 230 remains unchanged, pressure and temperature of the working medium 10 rise in the hot region 220. In particular, in a process with phase transformation of the working medium, a strong increase in pressure can take place when the liquid working medium evaporates. At the end of this first step, therefore, there are cold working medium under relatively low pressure in the cold region 110 of the first volume 100 and hot working medium in the hot region 220 of the second volume 200 under high pressure.
  • FIG. 19 now shows a next state of the pressure generator according to FIG. 18.
  • the valve 445 which is still blocking in FIG. 18 has been turned on, so that a fluid connection with the high-pressure side 310 of the working machine 300 is established between the connection 234 of the hot region 220 .
  • the valve 410 is turned on, between the low pressure side 320 of the engine 300 via the valve 430 and the control valve 420, fluid communication with the port 132 of the cold region 110 of the first volume 100 is established.
  • a fluid connection is thus established between the hot region 220 of the second volume 200 and the cold region 110 of the first volume 100.
  • the hot working medium 10 Due to the pressure difference, the hot working medium 10 now flows from the hot area 220 into the cold area 110. In doing so, the flowing medium on the machine 300 performs mechanical work that can be removed in this way.
  • Fig. 20 now shows a state of the pressure generator following the state shown in Fig. 19.
  • the control valve 420 is switched such that a fluid connection is established between the connection 132 of the cold region 110 and the connection 134 of the hot region 120.
  • the control valve 425 is switched to establish fluid communication between the hot region 220 and the cold region 210. It should be noted that in this way also a possibly existing pressure difference between the hot area 120 and the cold area 110 of the first volume 100 and the hot area 220 and the cold area 210 of the second volume 200 is compensated, so that the respective hot and cold regions of the first volume 100 and the second volume 200 have the same pressure level.
  • Fig. 21 now shows the next step in the operation of the pressure generator.
  • the displacement piston 140 is moved from the hot side 120 to the cold side 110.
  • the working medium previously located in the cold region 110 is thereby displaced via the established fluid connection into the hot region 120 of the first volume. Since the cold region 110 and the hot region 120 have no pressure difference, the displacer 140 does not have to work against pressure. The method of the displacer 140 thus requires only a small amount of energy to overcome bearing and frictional forces.
  • the displacement piston 240 is now moved from the cold region 210 into the hot region 220.
  • the displacement piston 240 is now moved from the cold region 210 into the hot region 220.
  • the pressure equalization between the hot area 220 and the cold area 210 no pressure work to be done.
  • the working medium 10 is thereby displaced from the hot region 220 into the cold region 210.
  • the fluid connection between the hot region 120 and the cold region 110 or, respectively, between the cold region 210 and the hot area 220 is locked so that the working media are respectively locked in the chamber 130 of the hot area 120 and the chamber 230 of the cold area 210.
  • the working medium is now heated in the first volume, namely in the hot region 120, and cooled in the second volume, namely in the cold region 210.
  • the hot volume is 120 of the first volume 100 hot and under high pressure working medium, while in the cold region 210 of the second volume is 200 cold and low pressure working medium.
  • the port 134 of the first volume hot region 120 is connected to the high pressure input 310 of the engine 300.
  • the port 232 of the cold region 210 is connected to the low pressure side 320 of the engine. Due to the pressure difference between the high-pressure working medium in the hot region 120 and the low-pressure working medium in the cold region 210, the working medium flows from the hot region 120 into the cold region 210 until the pressure difference is equalized. In this case, the flowing working medium performs mechanical work on the machine 300, which can be removed there.
  • control valves 420 and 425 are set analogously to FIG. 20 such that between the hot region 120 and the cold region 110 of the first volume and the cold region 210 and the hot region 220 of the second Volume fluid connection and thus a pressure equalization is produced.
  • the displacement piston 140 is now displaced again from the cold region 110 of the first volume into the hot region 120.
  • the displacer 240 is displaced from the hot region 220 into the cold region 210.
  • the working medium 10 in the cold region 110 of the first volume 100 is therefore now cooled and heated the working fluid in the hot region 220 of the second volume.
  • the pressure generator is now in the initial state shown in Fig. 18, so that the process can be performed again.
  • hot working fluid flows from the hot area 220 into the cold area 110.
  • the hot working medium flows through the regenerator 150, which absorbs and stores heat. If cooled working medium is now displaced from the cold region 110 into the hot region 120 in the step shown in FIG. 21, the cooled working medium is guided via the regenerator 150.
  • the working fluid already absorbs heat and is thus preheated before it enters the hot region 120. If the working medium is, for example, an ORC medium, in particular a low-temperature ORC medium, at least partial evaporation of the ORC medium can already take place in the regenerator 150. Likewise, the regenerator 150 is cooled again.
  • the regenerator 250 flows through, absorbing and storing heat. If, in the step shown in FIG. 25, the cooled working medium is now moved from the cold region 210 into the hot region 220, it absorbs heat stored there by the regenerator 250, cools it and reaches the hot region 220 preheated. Through the use of the regenerators 150, 250, the efficiency of the pressure generator can be increased.
  • Fig. 26 shows a heat engine and a pressure generator according to another embodiment of the present invention.
  • further heat exchangers 160, 260 are provided. These heat exchangers 160, 260 are traversed by a heating medium, which typically has a lower temperature than the heating means in the hot areas 120, 220.
  • a heating medium typically has a lower temperature than the heating means in the hot areas 120, 220.
  • the heat exchanger (s) 160, 260 may be provided as an alternative or in addition to the regenerators 150, 250.
  • both regenerators and heat exchangers are provided.
  • the working medium cooled in the cold region 110 can be brought to a temperature of, for example, 60 ° C. during the displacement via the regenerator 150.
  • the heating medium flowing through the additional heat exchanger 160 eg cooling water
  • a switch (not shown) can be provided, which alternately provides the second heating means to one of the heat exchangers 160, 260 when it is needed there.
  • Fig. 27 shows a heat engine or a pressure generator according to another embodiment of the present invention.
  • the first volume 100 is designed as a cylinder, which is passed through concentrically by a tube 112. Coolant 20 can be fed into the tube 112 via a coolant inflow 114. The coolant 20 exits at the outlet 118 of the tube 112 again.
  • the first volume 100 thus surrounds the tube 112, although more complex geometries can be selected to increase the heat exchange available surface area between the first volume 100 and the coolant tube 112.
  • the second volume 200 is designed as a cylinder, which is passed through concentrically by a tube 222. Via a Walkerstoffzufluß 224 heating means 30 can be fed into the tube 222. The heating means 30 exits at the outlet 228 of the tube 222 again.
  • the two tubes 112 and 222 each form at least a part of a heat exchanger for heat exchange between the heating means 30 and the coolant 20 and the working medium 10.
  • the device comprises a distributor disc 1210, which is rotatably mounted about an axis 1215.
  • the distributor disk 1210 comprises a heating medium line 224 and a coolant line 114.
  • a heating medium supply and a coolant supply are arranged coaxially to the axis 1215 of the distributor disk 1210 at an input of the distributor disk 1210.
  • the heating medium line abuts the one surface of the distributor plate 1210 with a flange.
  • the coolant line is guided centrally into the interior of the disk 1210.
  • the distributor disc 1210 comprises channels which divide the externally coaxially fed Banksch- and coolant flows and leads to each other in the diameter of the disc opposite outlets. This is illustrated in FIG.
  • the distributor disk can be rotated about its central axis 1210 so that the heating medium line 224 and the coolant line 114 exchange places with each other.
  • the tube 112 of the first volume 100 and the tube 222 of the second Volume 200 alternately with heating means 30 or coolant 20 are charged.
  • the tubes 112, 222 are therefore not clearly classified as heating or coolant tubes, since they alternately assume both functions.
  • a linear generator 300 operable with the pressure of the working medium is arranged on the central axis 1210.
  • the linear generator 300 in this case has a high-pressure side 310, which can be acted upon by heated working medium under high pressure.
  • the linear generator 300 has a low pressure side 320 that can be connected to the first volumes that have cooled and thus less pressurized working fluid.
  • Optionally connecting the first and second volumes to the high pressure side 310 and low pressure side 320 of the linear generator 300 is enabled by the valves 450, 455, 460, and 465 in the example shown.
  • a piston 330 is provided which has a plurality of magnets 335.
  • the piston 330 is moved toward the low pressure side 320.
  • the magnets 335 induce in the outer coil or the outer coils 340 of the linear generator, a voltage that can be tapped. Furthermore, the movement of the piston 330 presses any existing working fluid 12 via the valve 455 into the first volume 100.
  • the distributor disc 1210 can now be rotated as shown in FIG. 28, with the linear generator 300 fixed.
  • the high pressure side and the low pressure side are reversed, so that the piston 330 is displaced to the opposite axial end of the linear generator.
  • the process may start over again, with the control of the valves 450, 455, 460, 465 each determining whether a volume is connected to the high pressure side 310 or the low pressure side 320 of the linear generator 300.
  • the device can also be operated in such a way that a phase transition occurs on cooling and heating of the working medium.
  • an ORC medium or water can be used.
  • the gas or vapor phase ORC medium is liquefied on cooling.
  • a dramatic reduction in volume of the working medium occurs, so that a negative pressure is practically generated in the cooled volume.
  • the working medium flowing out of the hot volume condenses on entry into the cold region, so that substantially no pressure equalization is produced between the first and the second volume.
  • the liquid working fluid is evaporated on heating, whereby the volume multiplies or the pressure increases considerably.
  • the apparatus described above can be used in a variety of fields, namely wherever waste heat is available. In particular, this is naturally the case in all combustion processes, for example in engines, biogas cogeneration plants, power plants, etc. However, waste heat is also produced in many other technical processes, for example in steel production and processing, plastics processing and cement production. In all these processes, the device can be used to harness the waste heat often wasted to save energy and increase the efficiency of the processes. In particular, the device can also be used for the use of waste heat in heating systems in residential areas, such as central heating or the like. In such systems, a burner temperature of 800-900 ° C is reached, with typical flow temperatures for space heaters are only 60 ° C. The high temperature difference can be made available by means of the pressure generator for power generation. Equally applicable is the above-described pressure generator in the field of combustion of renewable raw materials, in particular Holzpellet- or wood heating or fireplaces. The combustion of wood gas can also serve to generate the required waste heat.
  • FIG. 29 shows a schematic representation of a device or a heat engine 1000 according to a further exemplary embodiment of the present invention.
  • the first volume 100 has a Bankffenanschluß 124 which is connectable to a line for a waste heat-carrying heating medium.
  • the first volume 100 to a coolant port 114, which with a Line for a coolant is connectable.
  • the heating means can exit via a Walkerstoffauslass 128 and the coolant via a coolant outlet 118 again from the first volume 100.
  • the second volume 200 has a heating means port 224 which is connectable to a waste heat carrying heating pipe.
  • the second volume 200 also has a coolant connection 214, which can be connected to a line for a coolant.
  • the heating medium can exit from the second volume 200 via a heating medium outlet 228 or the coolant via a coolant outlet 218.
  • the first volume 100 and the second volume 200 are connected to one another via a fluid line 400 in such a way that working medium can be exchanged between the two volumes and thereby work on a machine 300.
  • Figure 30 shows a schematic representation of a system according to an embodiment of the present invention.
  • the system comprises a first device or heat engine 1000 and a second device or heat engine 2000.
  • the first and the second device 1000, 2000 are formed according to the device shown in FIG.
  • the heating medium connection 124 of the first volume 100 of the second device 2000 is connected to a heating medium outlet 128 of the first volume 100 of the first device 1000.
  • the coolant port 114 of the first volume 100 of the second device 2000 is not connected to the coolant outlet 118 of the first volume 100 of the first device 1000.
  • the heating medium connection 224 of the second volume 200 of the second device 2000 is connected to the heating medium outlet 228 of the second volume 200 of the first device 1000.
  • the coolant port 214 of the first volume 100 of the second device 2000 is not connected to the coolant outlet 218 of the first volume 100 of the first device 1000.
  • the first device 1000 may be configured for a high-temperature process.
  • Typical heater input temperatures at the heater ports 124, 224 of such a high temperature process are in the range of about 400 ° C to about 900 ° C.
  • Typical heater output temperatures at the heater outlets 128, 228 range from about 200 ° C to about 400 ° C.
  • high temperature differences .DELTA.T can be used in the device become. This typically occurs in a pure gas process, for example with helium, and high process pressures in the range of several hundred bar.
  • the second device 2000 is adapted for a process that has a lower process temperature compared to the process performed in the first device 1000.
  • the first device 1000 may be set up instead of a high-temperature process for such a medium-temperature process.
  • Typical Schuffenausgangstemperaturen are then in the range of about 100 ° C to about 200 0 C.
  • the thereby attainable temperature difference .DELTA.T for example, efficiently by Operation of the device 2000 can be used with an ORC medium. In this case, typically a phase transformation of the ORC medium is brought about during the process.
  • other working media such as water, can be used.
  • the first apparatus 1000 and the second apparatus 2000 each include a machine 300.
  • the machines 300 and / or the processes run in the devices 1000, 2000 can be coordinated with one another in such a way that the machines 300 are harmonized or synchronized with one another.
  • the two machines 300 may be designed as motors. In this case, both motors 300 can be set up so that they drive the same shaft together.
  • Fig. 31 is a schematic diagram of another system according to an embodiment of the present invention.
  • the basic structure of the system according to FIG. 31 corresponds to the system shown in FIG.
  • the first device 1000 and the second device 2000 are connected to the same machine 300.
  • the system can be set up such that the first and the second device 1000, 2000 can be operated out of phase with one another.
  • the first and second devices 1000, 2000 may each be at a given time different cycles of the process.
  • it can be delivered to the machine (s) 300 with deferred displacement of the clocks of the respective devices to each other constantly.
  • Fig. 32 is a schematic diagram of still another system according to an embodiment of the present invention.
  • the system shown therein also includes a third heat engine 3000, wherein the heater ports 124, 224 of the third device 3000 are connected to the heater outlets 128, 228 of the second device 2000.
  • the third device 3000 is set up for a process which, compared to the second device 2000, has an even lower process temperature.
  • Typical heater input temperatures for this low temperature process range from about 80 ° C to about 200 ° C.
  • Typical Schuffenausgangstemperaturen for this low temperature process are in the range of about 2O 0 C to about 100 ° C.
  • a low-temperature ORC medium can be used in this temperature range, with the low-temperature ORC medium undergoing a phase transformation in the process.
  • the first apparatus 1000, the second apparatus 2000, and the third apparatus 3000 each include a machine 300.
  • the machines 300 and / or the processes run in the devices 1000, 2000, 3000 can be coordinated with one another in such a way that the machines 300 are harmonized or synchronized with one another.
  • the three machines 300 may be configured as motors. In this case, all motors 300 can be set up so that they drive the same shaft together.
  • FIG. 33 shows a schematic representation of yet another system according to an exemplary embodiment of the present invention.
  • the basic structure of the system according to FIG. 33 corresponds to the system shown in FIG. 32.
  • the first device 1000, the second device 2000 and the third device 3000 are connected to the same machine 300.
  • the system can be set up that the first, the second and the third Heat engine 1000, 2000, 3000 can be operated out of phase with each other.
  • the first, second, and third heat engines 1000, 2000, 3000 may be at different times in the process at a given time.
  • it can be delivered to the machine (s) 300 with deferred displacement of the clocks of the respective heat engines to each other constantly.
  • the cascaded systems described above use two, three, or more stages, each of which uses the waste heat still contained in the cooled heating means leaving one stage in the next stage.
  • the different stages are coordinated so that the respective subsequent stage is adapted by their process forth to the temperature of the emerging from the previous stage heating medium.
  • the working media are coordinated with each other.
  • the amounts, volumes, geometries and / or the construction of the respective stages can be adapted to the respective process temperatures of a stage.
  • the types and working media can differ between different levels.
  • Fig. 34 is a schematic diagram of a system according to another embodiment of the present invention.
  • the system has a first device or heat engine 1000 described above and at least one second device or heat engine 2000 described above.
  • the heating medium connection of the first volume 100 of the first device 1000 and the heating medium connection of the first volume 100 of the second device 2000 are connected to the same heating medium line 124.
  • the heating medium connection of the second volume 200 of the first device 1000 and the heating medium connection of the second volume 200 of the second device 2000 are connected to the same heating medium line 124.
  • the heating medium supply line 124 for the first volumes 100 and the heating medium supply line 224 for the second volumes are also connected to the same heating medium line, for example an exhaust line.
  • the system is set up so that the first and the second device 1000, 2000 can be operated out of phase with each other so that the first device 1000 and the second device 2000 are in different cycles.
  • the first device 1000 and the second device 2000 may have a motor as a machine and wherein the respective motors are arranged so that they drive the same shaft.
  • the first device 1000 and the second one may also be used Device 2000 may be connected to the same machine 300.
  • both devices 1000, 2000 run side by side at the same stage, ie the heating means has the same inlet temperature in both devices 1000, 2000. It is not necessary, however, typical that in this case the same process is used in both devices 1000, 2000.
  • each of the previously described cascaded systems at each stage may have multiple devices connected in parallel.
  • the number of devices connected in parallel may be the same or different from stage to stage of the cascaded system.
  • Fig. 35 shows a plant according to another aspect of the invention.
  • the system comprises an internal combustion engine 1100, in particular a motor, and a device or a system described above. Via a fuel supply 1110 fuel is supplied to the internal combustion engine 1100 and burned there.
  • the internal combustion engine drives an external machine G.
  • the exhaust gas produced in the combustion is fed via an exhaust gas outlet 1120 in the heating medium line 126, where the waste heat contained in it is then used in the manner described above by the downstream device or the system.
  • the exhaust gas can also be alternatively led into a further heat exchanger 1140, in which the exhaust gas heats the actual heating means for the downstream device.
  • the exhaust gas is then removed via a conventional exhaust system.
  • water or, in particular, a thermal oil can be used as the heating medium, in which case a countercurrent heat exchanger is typically used.
  • a countercurrent heat exchanger is typically used.
  • interposing the heat exchanger can be avoided on the one hand so that the engine exhaust pollutes the heat exchanger of the downstream device.
  • the engine is used with a motor operated with biodiesel 1100, such contamination is virtually unavoidable.
  • temperature peaks in the exhaust gas can be absorbed by the thermal oil. This is particularly advantageous if an ORC process is run in the downstream device. Otherwise there would be the danger that the ORC medium would decompose at such temperature peaks if the device were charged directly with the exhaust gas.
  • the internal combustion engine 1100 has a radiator 1130.
  • the coolant heated in the cooler for example cooling water, is admitted via a cooling water line 1135 the heat exchangers 148, 248 passed.
  • the engine cooling water can be used for intermediate heating of the working medium.
  • the internal combustion engine 1100 is a diesel engine of a combined heat and power plant.
  • the diesel engine 1100 drives an electric generator G and thus generates electricity.
  • the discharged from the diesel engine exhaust gas 1100 is supplied as a heating means a cascaded system, where it enters with about 45O 0 C in the first stage.
  • the engine exhaust heat is removed to operate the device (s) of the first stage, so that the exhaust gas at about 25O 0 C leaves the first stage of the system.
  • the exhaust gas now enters a second stage of the system at about 25O 0 C.
  • the engine exhaust already cooled in the first stage, further heat to operate the device (s) of the second stage is withdrawn, so that the exhaust gas leaves with about 12O 0 C, the second stage of the system.
  • a high-temperature ORC process with high-temperature ORC media that are even chemically stable at the process temperatures in the range of 200 0 C driven.
  • the high temperature ORC process can now be followed by a third stage in which a low temperature ORC process is run.
  • the cooled in the first and second stage exhaust gas now enters with about 12O 0 C in the third stage, where it is deprived of heat and it leaves the third stage with about 7O 0 C.
  • This low temperature ORC process is operated at a low temperature ORC medium containing, for example, already evaporated at about 2O 0 C and 5O 0 C,.
  • heat exchangers 148, 248 are flowed through by the approximately 90 0 C hot engine cooling water.
  • the cooled working medium can already be preheated or reheated. In this way, even a part of the waste heat contained in the cooling water can be recovered.
  • regenerators can be used in all or in individual stages, store the heat and serve to preheat the cooled working medium.
  • Fig. 36 shows a cross-sectional view of an electric generator 300 as it can be used as an engine in an embodiment of the present invention.
  • the electric generator 300 in this case has a piston chamber 610, which has an inlet opening 612 and an outlet opening 614.
  • the piston chamber 610 is annular in the cross-sectional view shown.
  • a piston 620 is further arranged, which is rotatably mounted about the center of the annulus.
  • the piston 620 has a pressure side 622, which communicates with the pressurized working fluid, the over Inlet opening 612 can be inserted into the piston chamber 610, can be acted upon.
  • the piston 620 is connected to a rotatably mounted ring 635.
  • Magnets 630 are arranged on the ring 635, with the magnetic poles alternating in the circumferential direction adjacent magnets. This is indicated in Fig. 36 by the corresponding arrows.
  • the magnets 630 can be attached to the ring 635 or integrated in this.
  • the magnets 630 may be formed as permanent magnets or as electromagnets. In the latter case, the electric generator 300 has a power supply to the electromagnets 630. This can be done for example via slip rings and brushes.
  • the ring 635 is disposed on the inner circumference of the piston chamber 610. Opposite him coils 640 are arranged. Now, when the magnets 630 are moved past the coils 640, they induce a voltage in these coils. This voltage can be tapped and the electric generator 600 thus electrical power can be removed.
  • a stationary seal 660 is arranged between the ring 635 and the coils 640.
  • the stationary seal 660 gas-tightly seals the piston chamber 610 from the coils 640.
  • a movable seal 650 is provided between the inlet opening 612 and the outlet opening 614. As indicated by the double arrow in Fig. 36, the movable seal 650 can be moved in the radial direction. In this case, the movable seal 650 can be moved from the piston chamber into a radially outer receptacle and from this back into the piston chamber.
  • the movable seal 650 is configured to substantially close the piston chamber 610 between the inlet port 612 and the outlet port 614 in a pressure-tight manner.
  • a gap is created between the pressure side 622 of the piston 620 and the movable seal 650 into which a working medium can be introduced via the inlet opening 612.
  • an intake valve 670 and an exhaust valve 680 are shown. Via the inlet valve 670, the introduction of working fluid into the piston chamber 610 can be controlled. At the same time, discharge of working fluid from the piston chamber 610 can be controlled via the outlet valve 680.
  • FIG. 37 shows a cross-sectional view of a rotary piston engine 300 that may be used as a machine according to another embodiment of the present invention.
  • the rotary piston engine 300 in this case has a piston chamber 710, the one Inlet opening 712 and an outlet 714 has.
  • the piston chamber 710 is annular in the cross-sectional view shown.
  • a piston 720 is further arranged, which is rotatably mounted about the center of the annulus.
  • the piston 720 has a pressure side 722, which can be acted upon by a pressurized working fluid, which can be introduced into the piston chamber 710 via the inlet opening 712.
  • the piston 720 is connected to a rotatably mounted piston ring 735.
  • first magnets 730 are arranged, wherein the magnetic poles alternate in the circumferential direction adjacent magnets. This is indicated in Fig. 37 by the corresponding arrows.
  • the first magnets 730 can be attached to the piston ring 735 or integrated therein.
  • the first magnets 730 may be formed as permanent magnets or as electromagnets. In the latter case, the rotary piston engine 300 has a power supply to the electromagnets 730. This can be done for example via slip rings and brushes.
  • the piston ring 735 is disposed on the inner circumference of the piston chamber 710. Opposite him second magnets 740 are arranged.
  • the second magnets 740 are arranged on a drive ring 745, wherein the magnetic poles alternate in the circumferential direction adjacent to each other second magnet.
  • the second magnets 740 cover the entire periphery of the drive ring 745.
  • the first magnets 730 and the second magnets 740 form a magnetic coupling. Now, when the first magnets 730 are rotated with respect to the second magnets 740, the first magnets take with them the second magnets due to the magnetic forces acting therebetween. In this way, the rotation of the piston 720 can be transmitted to the drive ring 745.
  • the drive ring 745 forms in the embodiment shown in Fig. 37, the ring gear of a planetary gear, which further includes the planet gears 746 and the sun gear 748.
  • a motor shaft 770 is connected to the sun gear 748.
  • the rotary piston 720 drives the motor shaft 770 via the magnetic coupling 735, 745 and the planetary gear 745, 746, 748.
  • the planetary gear desired over or speed ratios between the piston 720 and motor shaft 770 can be adjusted. For example, by means of the transmission at the engine output shaft, a speed in the range of 1500 rpm, which is suitable for driving conventional electric generators, can be provided.
  • a stationary seal 760 is arranged between the Kolbening 735 and the drive ring 745 arranged between the Kolbening 735 and the drive ring 745 .
  • the stationary seal 760 seals the piston chamber 710 against the drive ring 745 gas-tight. Furthermore, a movable seal 750 is provided between the inlet port 712 and the outlet port 714. As indicated by the double arrow in Fig. 37, the movable seal 750 can be moved in the radial direction. In this case, the movable seal 750 can be moved from the piston chamber into a radially outer receptacle and from this back into the piston chamber. The movable seal 750 is configured to substantially close the piston chamber 710 between the inlet port 712 and the outlet port 714 in a pressure-tight manner.
  • a gap is created between the pressure side 722 of the piston 720 and the movable seal 750 into which a working medium can be introduced via the inlet opening 712.
  • an intake valve 790 and an exhaust valve 795 are shown. Via the inlet valve 790, the introduction of working fluid into the piston chamber 710 can be controlled. At the same time, discharge of working fluid from the piston chamber 710 can be controlled via the outlet valve 795.
  • Fig. 38 shows a schematic representation of an arrangement in which two motors 800, 900 of the type described above are connected in series.
  • a single motor 700 in embodiments of the present invention, of course, a combination of two or more motors or even two or more generators can be used.
  • the outlet 814 of the first motor 800 is connected to the inlet 914 of the second motor 900.
  • the working medium flowing out of the first motor 800 can still be used in the second motor 900 to drive a common motor shaft.
  • the second motor 900 can now be operated with optimized efficiency, so that the lower Pressure working fluid in the second motor 900 is as completely relaxed.
  • the cross sections or volumes of the two motors can be adapted to each other in a suitable manner.
  • the high-power, high-pressure engine 800 may have a small cross-section of the piston chamber, whereas the cross-section of the piston chamber of the second motor 900 may be correspondingly larger to reduce the amount of working fluid from the piston first motor 800 to record and relax.
  • more than two motors can be connected in a suitable manner one behind the other, wherein the respective cross sections / volumes or motor diameters are to be matched to one another.
  • such multi-stage motors can be arranged in a single housing, so that a compact multi-stage design is provided.
  • the controls of the inlet and outlet valves and, if appropriate, the controls of the excitation currents for magnetic coils can also be coordinated with one another.
  • Such a multi-stage design can be operated in wide pressure ranges and the various operating parameters can be set almost arbitrarily. Other degrees of freedom of the system can be set, for example, by providing intermediate heating of the working medium between two motor stages or similar comparable measures. Of course, such a concept can be implemented on two cascaded generators in the same or similar manner.
  • FIG. 39 Shown therein is a heat engine having two substantially equally constructed units. In this case, all dimensions, in particular volumes, of the two units may be the same or different from each other.
  • the first unit comprises a first radiator K1 and a first evaporator B1, B2.
  • the first cooler Kl is essentially a pressure-tight container, which is penetrated by coolant tubes Rl.
  • the first evaporator comprises a first volume Bl and a second volume B2, wherein the first volume Bl is typically smaller than the second volume B2.
  • the first and second volumes Bl, B2 are connected to each other via a fluid line F7. In the fluid line F7, a valve V7 is further arranged, so that the fluid line F7 can be shut off.
  • the valve V7 By means of the valve V7 so the first volume Bl and the second volume B2 are to be separated from each other.
  • the first evaporator is penetrated by Schuffenrohren Hl, wherein the Schuffenrohre Hl are arranged so that they first pass through the first Bl of the first evaporator in the direction of flow of the heating medium and subsequently pass through the second volume B2 of the first evaporator in the direction of flow of the heating medium.
  • the heating medium thus first flows through the first volume B1, discharges a portion of its heat there and then flows through the second volume B2 at a somewhat lower temperature, where it is deprived of further heat.
  • the first volume Bl of the evaporator is connected via a first fluid line Fl with the first cooler Kl, wherein the first fluid line Fl can be shut off by means of a first valve Vl. Furthermore, the first cooler Kl is disposed above the first volume Bl. In this way, condensed liquid can be returned to the condenser in the condenser Kl, wherein the condensed liquid flows back due to the gravitational force in the evaporator. It can therefore be dispensed with entirely in the present arrangement, a pump or similar means, since only the gravitational force is sufficient to allow the condensed and cooled liquid to flow back into the first volume Bl.
  • the second unit comprises a second radiator K2 and a second evaporator B3, B4.
  • the second radiator K2 is essentially a pressure-tight container, which is penetrated by coolant tubes R2.
  • the second evaporator comprises a third volume B3 and a fourth volume B4, wherein the third volume B3 is typically smaller than the fourth volume B4.
  • the third and the fourth volume B3, B4 are connected to each other via a fluid line F8.
  • a valve V8 is further arranged, so that the fluid line F8 can be shut off. By means of the valve V8, therefore, the third volume B3 and the fourth volume B4 are to be separated from each other.
  • the second evaporator is penetrated by Schuffenrohren H2, wherein the Schuffenrohre H2 are arranged so that they first pass through the third volume B3 of the second evaporator in the direction of flow of the heating medium and subsequently prevail in the flow direction of the heating medium, the fourth volume B4 of the second evaporator.
  • the heating medium thus first flows through the third volume B3, discharges a portion of its heat there and then flows through the fourth volume B4 at a somewhat lower temperature, where it is deprived of further heat.
  • the third volume B3 of the evaporator is connected via a fourth fluid line F4 to the second radiator K2, wherein the fourth fluid line F4 can be shut off by means of a second valve V2.
  • the second radiator K2 is arranged above the third volume B3. In this way, condensed liquid can be returned to the evaporator in the cooler K2, wherein the condensed liquid flows back into the evaporator due to the gravitational force. It can therefore be dispensed with entirely in the present arrangement to a pump or similar means, since only the gravitational force is sufficient to to let the condensed and cooled liquid flow back into the third volume B3.
  • the heat engine further comprises a machine M operable with a fluid under pressure.
  • the machine M is connected to the first volume Bl via a second fluid line F2 and to the first radiator Kl via a third fluid line F3. Furthermore, the machine M is connected to the third volume B3 via a fifth fluid line F5 and to the second radiator K2 via a sixth fluid line F6.
  • the machine M may be, for example, a motor, a generator, a turbine or the like. In particular, the machine can operate on the rotary piston principle as a rotary piston engine.
  • the fluid lines connected to the machine M can each be shut off via valves.
  • the second fluid line F2 can be shut off via a third valve V3 and the third fluid line F3 via a fourth valve V4.
  • the fifth fluid line F5 can be shut off via a fifth valve V5 and the sixth fluid line F6 can be shut off via a sixth valve V6.
  • the first evaporator and the second evaporator are at least partially filled with a liquid to be evaporated, for example water or an ORC medium.
  • a liquid to be evaporated for example water or an ORC medium.
  • the second and the fourth volume B2, B4 are completely filled with the liquid while the first and the third volume Bl, B3 are only partially filled with the liquid.
  • the operation of the system will now be explained by the operation of the first unit.
  • the first valve Vl and the third valve V3 are closed while the seventh valve V7 is opened.
  • the liquid contained in the first volume Bl is heated by the flowing in the heating tubes Hl heating medium, such as exhaust gas, and finally evaporated.
  • the third valve V3 and the fourth valve V4 are opened.
  • the vaporized liquid then flows via the second fluid line F2 into the machine M, performs work there and flows via the third fluid line F3 into the first condenser K1.
  • the first condenser K1 flows through a cooling medium in the cooling tubes R1.
  • the cooling medium extracts heat from the steam and cools the steam until the liquid condenses. Due to gravity, the liquid collects at the bottom of the radiator K1 and abuts the valve Vl. Now, if the pressurized steam escaped from the first volume Bl, the third valve V3 and the seventh valve V7 are closed and the first valve Vl is opened. Under the influence of gravity, the cold liquid from the first cooler Kl now flows into the first volume B1.
  • valve Vl is closed and the seventh valve V7 is opened again. Now, heated liquid from the second volume B2 flows into the first volume Bl. After a short time, a pressure equalization between the first and the second volume Bl, B2 has set and the entire process described above can start all over again. Exactly the same process takes place in the second unit, but the processes are clocked so staggered that the machine M is operated alternately with steam from the first evaporator B 1 and from the second evaporator B3.
  • the vapor from the first evaporator Bl in the second radiator K2 and the steam from the second evaporator B3 is passed into the first radiator Kl.
  • the fourth valve V4 but the sixth valve V6 is opened.
  • the steam flows from the first volume Bl via the engine M into the second radiator K2, where it condenses and collects at the bottom.
  • the fifth valve V5 and the fourth valve V4 are opened so that the steam from the second evaporator flows into the first radiator. So you could say that the system is operated in this mode "cross".
  • the second and fourth volumes B2, B4 provided in the illustrated embodiment may also be omitted. In the exemplary embodiment shown, however, they serve as heat storage and continuously remove heat from the heating medium, whereby a temperature gradient running from top to bottom in the second or fourth volume B2, B4 sets. During the evaporation phase, the liquid contained in the second and fourth volumes B2, B4, respectively, continues to absorb heat, so that it is typically just below its boiling point.

Abstract

L'invention concerne une machine thermique (1000) comprenant un premier volume (100) qui est agencé pour être alternativement chauffé et refroidi, un second volume (200) qui est agencé pour être alternativement chauffé et refroidi, un milieu de travail (10) qui est contenu dans le premier et dans le second volume (100, 200), et une conduite de fluide (400) au moyen de laquelle le premier volume (100) et le second volume (200) sont reliés entre eux. L'invention est caractérisée en ce qu'une machine (300) capable de fonctionner avec le milieu de travail est reliée, entre le premier volume (100) et le second volume (200), avec la conduite de fluide (400), en ce que la machine thermique (1000) est agencée de façon que, dans un premier état, le milieu de travail (10) dans le premier volume (100) est chauffé, tandis le milieu de travail (10) dans le second volume (200) est refroidi, et en ce que, dans un second état, le milieu de travail (10) dans le premier volume (100) est refroidi, tandis que le milieu de travail dans le second volume (200) est réchauffé.
EP09740076A 2008-09-24 2009-09-24 Machine thermique et procédé permettant de la faire fonctionner Withdrawn EP2326821A2 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE200810048641 DE102008048641B4 (de) 2008-09-24 2008-09-24 Druckerzeuger
DE200810048633 DE102008048633B4 (de) 2008-09-24 2008-09-24 Vorrichtung und Verfahren zur Umwandlung von Abwärme
DE200810048639 DE102008048639B4 (de) 2008-09-24 2008-09-24 Wärmekraftmaschine und Verfahren zum Betreiben derselben
PCT/EP2009/062396 WO2010034780A2 (fr) 2008-09-24 2009-09-24 Machine thermique et procédé permettant de la faire fonctionner

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EP2326821A2 true EP2326821A2 (fr) 2011-06-01

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EP (1) EP2326821A2 (fr)
WO (1) WO2010034780A2 (fr)

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Publication number Priority date Publication date Assignee Title
FR2963669A1 (fr) * 2010-08-06 2012-02-10 Jean Francois Chiandetti Echangeur thermique interne pour moteur a combustion externe, compresseur isotherme, pompe a chaleur et mecanisme refrigerant place au sein du volume de travail
DE102011104191B4 (de) 2011-06-14 2021-09-16 IdeTec GmbH Wärmekraftmaschine

Citations (2)

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JPS59119073A (ja) * 1982-12-24 1984-07-10 Toshiba Corp 低温度差発電プラント
WO2009138233A2 (fr) * 2008-05-15 2009-11-19 Maschinenwerk Misselhorn Gmbh Moteur thermique

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DE2543745A1 (de) * 1975-10-01 1977-04-07 Udo Voos Komplementaer-heissgasmotor
JPS6062609A (ja) * 1984-07-30 1985-04-10 Hitachi Ltd 冷熱発電装置
US7665304B2 (en) * 2004-11-30 2010-02-23 Carrier Corporation Rankine cycle device having multiple turbo-generators
DE102005013287B3 (de) * 2005-01-27 2006-10-12 Misselhorn, Jürgen, Dipl.Ing. Wärmekraftmaschine
US20070234719A1 (en) * 2006-04-06 2007-10-11 Alexander Schuster Energy conversion device and operation method thereof
DE102006028561B3 (de) * 2006-06-22 2008-02-14 KNÖFLER, Steffen Zwei-Zylinder-Hydrostirling-Maschine mit Hydraulikmotor
AT505645B1 (de) * 2007-09-11 2009-05-15 Schlager Leopold Wärmekraftmaschine
BE1017812A5 (fr) * 2008-01-09 2009-07-07 Cohen Albert Moteur pendulaire.
SE533122C2 (sv) * 2008-03-12 2010-06-29 Oerjan Forslund Omvandlare av solenergi till elektricitet

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JPS59119073A (ja) * 1982-12-24 1984-07-10 Toshiba Corp 低温度差発電プラント
WO2009138233A2 (fr) * 2008-05-15 2009-11-19 Maschinenwerk Misselhorn Gmbh Moteur thermique

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