Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
  • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
  • F01K27/005—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for by means of hydraulic motors
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
  • F01K13/00—General layout or general methods of operation of complete plants
  • F01K13/02—Controlling, e.g. stopping or starting
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
  • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
  • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
  • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
  • F01K25/103—Carbon dioxide

Definitions

• the present invention relates to a heat engine, in particular for the low-temperature operation for the utilization of solar heat, waste heat from biological or industrial processes or the like, with:
• At least two cylinder-piston units each containing a strain fluid under a biasing pressure, which changes its volume with a temperature change and thus moves the piston
• control means controlling the heat supply means for alternately heating and cooling each expansion fluid to thereby move the pistons
• Such a heat engine is known from WO 2009/082773.
• Effective expansion fluids often require a certain bias pressure to exhibit a significant coefficient of expansion in the desired operating temperature range.
• An example of this is liquid carbon dioxide, which under a pressure of about 60 - 70 bar when heated from 20 ° C to 30 ° C its volume changes by about 2.2 times.
• the common biasing fluid establishes a common, uniform biasing pressure in all of the cylinder-piston units by directly communicating with each other those cylinder chambers which face the cylinder chambers with the expansion fluids.
• the common biasing fluid achieves variable, dynamic coupling of the cylinder-piston units.
• the work of the cylinder-piston units is mechanically transferred to working pistons via piston rods. wear, which act on a common working fluid circulating in a hydraulic load circuit via check valves.
• the invention has the aim of simplifying the decoupling of the work from the cylinder-piston units of a heat engine of the type mentioned initially and thus to further increase their efficiency.
• biasing fluid is guided from the cylinder-piston units via first check valves to an input and via oppositely directed second check valves to an output of a hydraulic load in which it is subject to a pressure drop between input and output,
• control device is equipped with a first pressure gauge for the pressure of the biasing fluid at the outlet of the load, and
• control device controls the heating and cooling phases of the heat supply device at least in dependence on the measured output pressure in order to keep it within a predetermined first range
• expansion fluid contains liquid carbon dioxide and the lower range limit of said predetermined first range is greater than or equal to the condensing pressure of carbon dioxide at the operating temperature.
• Liquid carbon dioxide is due to its high thermal expansion coefficient at room temperature, especially for operation of the heat engine in the low temperature range for the use of solar heat, waste heat from biological or industrial processes or the like.
• carbon dioxide resulting from combustion processes can be used for useful secondary recycling, in which it does not cause any greenhouse effect that is harmful to the environment.
• the heat engine of the invention thus also makes a contribution to the bypass-friendly C0 2 sequestration in the sense of a "Carbon Dioxide Capture and Storage” (CSS) process.
• CCS Carbon Dioxide Capture and Storage
• the biasing fluid is used simultaneously as a working fluid and vice versa:
• a pressure difference can be obtained, which directly used for driving a hydraulic load and can be converted into mechanical work there.
• the control of the heating and cooling phases as a function of the measured output pressure of the hydraulic load see ensures that the biasing pressure reaches the required minimum biasing pressure for the operation of the expansion fluid at its low pressure level in any case.
• Said first predetermined range is selected so that its lower range limit is above the minimum biasing pressure of the expansion fluid.
• Number of cylinder-piston units, which are in the cooling phase at the same time increases when the output pressure falls below the predetermined first range, and decreases when the output pressure exceeds the predetermined first range. This allows the operation to be adapted to extremely fluctuating environmental conditions. For example, in the low-temperature morning or evening hours of a solar system, approximately the same number of cylinder piston units can be operated in the heating and cooling phases, whereas in the midday heat few are rapidly heated
• Cylinder-piston units face many slow-cooling cylinder-piston units.
• the fine adjustment control device can also shorten or lengthen each individual heating and / or cooling phase in order to control the output. gear pressure within the predetermined first range.
• control device is equipped with a second pressure gauge for the pressure of the biasing fluid at the input of the load and controls the heating and Abksselphasen the heat supply device also in dependence on the measured input pressure to this within a predetermined second range to keep.
• the pressure difference for the hydraulic load can be controlled so that it corresponds to the pressure drop across the load or the work converted in the load is controlled by presetting the pressure difference.
• the controller may preferably increase the number of cylinder-piston units that are at a time in the heating phase against the number of cylinder-piston units that are in the cooling phase at the same time when the input pressure falls below given second range, and decrease when the input pressure exceeds the predetermined second range.
• control device can also individually shorten or extend the heating and / or cooling phases in order to keep the inlet pressure within the predetermined second range.
• the inlet pressure is always above the outlet pressure due to the pressure drop across the hydraulic load, it may be provided in a simplified embodiment that the first and second areas are equal, resulting in a minimum limit for the outlet pressure and a maximum limit for the inlet pressure.
• the predetermined second area may be overlapping, then or at a distance from the first area, around individual minimum and maximum limits for the control of the inlet and outlet Building outlet pressures.
• the two areas are at a distance from each other.
• the lower limit of the second range differs from the upper limit of the first range by approximately the pressure drop across the load, so that a minimum pressure difference can be guaranteed for the load.
• the biasing fluid may be of any kind per se, for example compressed air.
• the biasing fluid is particularly preferably hydraulic fluid, resulting in a force-fitting and reliable pressure coupling. Preference is given to the input of the hydraulic load, a first elastic buffer and / or connected to the output of a second elastic buffer for the biasing fluid, so that short-term pressure fluctuations during switching operations or with tax-neungsungswendigen individual shortening or extensions of the heating and cooling phases temporarily absorbed can be.
• the loading of the pistons with the biasing fluid can be carried out in various ways, for example by mechanical coupling of separate hydraulic biasing cylinders to the cylinder-piston units.
• the pistons of the cylinder-piston units are preferably designed as double-acting pistons, on one side of which the expansion fluid acts and on the other side of which the prestressing fluid acts, which results in a particularly simple construction.
• a preferred embodiment of the invention is characterized in that the heat supply device for each cylinder-piston unit comprises a flowed through by a heat transfer medium heat exchanger, which is provided with a controlled by the control device check valve.
• the control device check valve By simply opening and closing the check valves, the times and durations of the heating phases can be specified, between which then the cooling phases arise.
• the cooling phases can be accelerated if the heat supply device preferably also has a device for forced comprise cooling of the expansion fluids in the cooling phases.
• the heat transfer medium is under pressure in the heating phase and the forced cooling device has a controllable pressure relief device for each heat exchanger.
• the heat transfer medium can be used simultaneously as a coolant, by causing it to cool down by releasing pressure.
• the pressure relief device comprises a negative pressure buffer, which can be connected via a controllable switching valve to the heat exchanger, whereby a sudden relaxation and thus particularly rapid cooling can be achieved.
• the cylinder-piston units can be equipped with their own device for forced cooling of the expansion fluids in the cooling phases, which is controlled directly by the movement of their pistons.
• a forced cooling device for the cylinder-piston units comprises:
• auxiliary cylinder piston unit driven by the cylinder-piston unit and having at least one cylinder space
• the container is connected via at least one by the piston movement of the cylinder-piston unit freewheelable check valve with said one cylinder chamber.
• the hitherto closed non-return valve is forcibly opened by appropriate control and the evaporation agent expands abruptly in the one auxiliary cylinder chamber, cools down thereby causing a forced cooling of the expansion fluid, which supports the retraction of the piston or accelerated.
• the container Preferably, provision is made for the container to be in fluid communication with the said one cylinder chamber of the auxiliary cylinder-piston unit via the other cylinder chamber and, downstream of it, the non-return valve.
• the evaporation agent is compressed during the retraction movement of the cooling expansion fluid, remains in the extended state in the compressed state and then relaxes abruptly by the forced opening of the check valves in the end position of the extension movement.
• the container is preferably directly - i. not over the other cylinder space - via the check valve with said one cylinder space of the auxiliary cylinder piston unit in flow connection.
• the check valve is arranged directly in the piston of the auxiliary cylinder-piston unit and controlled by the striking of the piston in its one end position, resulting in a very compact design.
• Cylinder-piston unit is axially assembled with its auxiliary cylinder-piston unit, with their pistons are connected to each other via a piston rod.
• the container is carried by the piston of the cylinder-piston unit and the flow connection from the container to the cylinder chamber (s) passes through the piston rod, resulting in a very compact construction and trouble-free integration of the forced cooling device using a minimum number - Moving parts achieved in the cylinder-piston units.
• Fig. 1 is a schematic diagram of a heat engine of the invention with four cylinder piston units;
• Figures 2a to 2c are timing diagrams of the control of the heat supply means and the resulting piston movements of the machine of Figure 1;
• FIG. 3 shows a block diagram of a practical embodiment of a heat engine according to the invention with two exemplary cylinder-piston units
• 4a and 4b are schematic diagrams of two different embodiments of cylinder-piston units with integrated auxiliary cylinder piston units as Zwangsabkühlein- direction.
• Fig. 1 shows a heat engine 1 with four cylinder piston units 2-5.
• Each cylinder piston unit 2-5 has a cylinder 6 in which a piston 7 between a retracted position (shown at 2) and an extended position (shown at 5) can move.
• the space 6 'in the cylinder 6 to the left side of each piston 7 is completely occupied by an expansion fluid 8.
• the expansion fluid 8 has a high coefficient of thermal expansion and expands when heated to move the piston 7 from the retracted to the extended position, or contracts as it cools to move the piston 7 back again.
• a mechanical stirring means (not shown) for the expansion fluid 8 can be arranged to improve the heat conduction therein.
• the expansion fluid 8 is liquid
• Carbon dioxide (C0 2 ) which at room temperature has a condensing pressure of about 65 bar.
• Liquid C0 2 shows in the range of 20 ° C to 30 ° C, a thermal expansion by about 2, 2 times.
• the piston 7 is biased or biased with a biasing pressure greater than or equal to the condensing pressure in the direction of the expansion fluid 8.
• the biasing pressure is exerted by a biasing fluid 9 acting in the space 6 "to the right side of each piston 7, ie, the side of each piston 7 facing away from the expansion fluid 8.
• the biasing fluid 9 - preferably a hydraulic oil - circulates in all the cylinder-piston units 2-5 common hydraulic circuit, which includes a hydraulic load 10.
• the hydraulic load 10 is in for example a hydraulic motor with an input 11 'and an output 11 ", which is flowed through by the biasing fluid 9 and the kinetic energy of the biasing force 9 in mechanical work for an output shaft 11 111 converts.
• a pressure drop ⁇ occurs between the input 11 'and the output 11 "of the load 10.
• any other type of hydraulic load 10 which can be driven with a pressure gradient ⁇ could also be used, as known in the art.
• the biasing fluid 9 is led from the cylinder-piston units 2-5 via a set of first check valves 12 'and a first manifold 13' to the input 11 'of the load 10, and from its output 11 "via a second manifold 13" and a set second Check valves 12 "back to the cylinder chambers 6" of the cylinder-piston units 2 - 5.
• Each individual cylinder-piston unit 2 - 5 is thus a first, in the direction of the space 6 "to the input 11 'back and in the reverse direction blocking check valve 12' assigned, as well as a from the output 11 "to the room 6" out, in the reverse direction blocking second check valve 12 ".
• the prestressing fluid 9 When a piston 7 (arrow 14 ') is extended, the prestressing fluid 9 thus establishes a first pressure level pi at the inlet 11' of the load 10 (inlet pressure) via the first check valves 12 'and the first manifold 13', so to speak as "working fluid” Retraction of the piston 7 (arrow 14 ") closes the respective first check valve 12 'and opens the respective second check valve 12", so that the reduced by the pressure drop ⁇ second pressure level p 2 from the output 11 "of the load 10 (" output pressure ") via the second manifold 13 "into the respective back-acting cylinder piston units 2-5 and biased the expansion fluid 8.
• the pressure of the biasing fluid 9 in the spaces 6 "of the cylinder-piston units 2 - 5 therefore oscillates between the input pressure (upper level) pi during extension (arrow 14 ') and the outlet pressure (lower level) p 2 during retraction (arrow 14 ").
• the lower pressure level, the output pressure p 2 , the biasing fluid 9 in any phase of movement 14 ', 14 "the necessary operating pressure for the biasing fluid 9, eg the liquefaction pressure of liquid C0 2 , below and at the same time the desired or required pressure difference ⁇ Pi - P 2 is maintained at the load 10.
• a first elastic intermediate store 15 ' can be connected to the input 11' or the collecting line 13 ', for example a pressure container with gas filling and / or with an elastic membrane 15 in order to buffer short-term pressure fluctuations.
• a second such elastic intermediate store 15 "to the output 11" or the collecting line 13 " it is also possible to connect a second such elastic intermediate store 15 "to the output 11" or the collecting line 13 ".
• the heating of the expansion fluids 8 in the cylinder-piston units 2 - 5 is caused by means of a controllable heat supply means 16 - 20.
• the heat supply device 16 - 20 comprises a heat exchanger 16 for each cylinder-piston unit 2 - 5, which contacts the expansion fluid 8 in a heat-conducting manner and in which a heat transfer medium 17 circulates.
• the heat transfer medium 17 is e.g. heated by a solar panel 18 in a heat transfer circuit 19 (returns in Fig. 1 for the sake of clarity not shown).
• the heat exchangers 16 may be of any type known in the art; Preferably, they are equipped with heat pipes for promoting the heat exchange and for the rapid and uniform distribution of the heat supplied in the expansion fluids 8.
• Each heat exchanger 16 is provided with a controllable check valve 20.
• the check valves 20 are alternately and intermittently opened by a central control means 21 to alternately heat and cool each cylinder-piston unit 2-5, thereby alternately expanding and contracting the expansion fluids 8 in the cylinders 6 and thus ultimately pushing the pistons 7 back and forth to move here.
• the piston movements are synchronized via the biasing fluid 9 circulating in the hydraulic circuit 10 - 13, in that the biasing fluid 9 flowing back from the outlet 11 'via the second check valves 12 "also assists and forces the retraction movement (arrow 14").
• the control device 21 actuates the check valves 20 as a function of measured values of the inlet pressure pi and preferably also of the outlet pressure p 2 which it receives from corresponding pressure gauges 22 ', 22 "which are connected to the inputs 11', 11" or their manifolds 13 ',
• a first, primary control target of the control device 21 is to keep the outlet pressure p 2 within a first predetermined range P2, min / P2, max, which is determined in particular by the minimum biasing pressure for the expansion fluid 8, eg (temperature-dependent) about 50 - 60 bar with liquid carbon dioxide in the temperature range 20 - 50 ° C.
• the lower limit p 2 , min of the first range is determined by the required minimum biasing pressure.
• control objectives of the control device 21 may be that at the same time care is taken that the input pressure pi is within a predetermined (second) range Pi, min, Pi, max.
• the first and second regions may be identical or partially overlapping or immediately adjacent to or spaced apart, in which latter case the output pressure p 2 is in a lower region (pressure band) and the input pressure pi is in an upper region (pressure band) ,
• the control device 21 can also control the pressure drop ⁇ of the load 10 in further control targets, see optional control line ei.
• the pressure ranges of input and output pressures pi, p 2 that can be achieved on the basis of the current temperature conditions can be used to calculate a useful pressure difference pi-p 2 and set this as the default for the pressure drop ⁇ at the load 10.
• the stated control objectives of the control device 21 are primarily with a control of the number of cylinder piston units 2 - 5, which are currently in the heating phase at a certain time, in relation to the number of those other cylinder piston units 2 - 5 , which are currently in the cooling phase at this time, achieved, as will now be explained in more detail with reference to FIG. 2.
• FIG. 2 a shows a first operating state of the heat engine 1 for ambient conditions in which the cooling phase of the expansion fluid 8 is about three times as long as the heating phase, for example because the temperature of the heat transfer medium 17 is high and causes a rapid heating.
• the check valves 20 are cyclically opened for about a quarter of the stroke period, respectively. As can be seen, are located at a given time always a cylinder-piston unit 2-5 in the heating phase and three others in the cooling phase, ie the ratio of expanding cylinder-piston units 2-5 to contracting cylinder-piston units 2 - 5 is 1: 3 here.
• 2 b shows a second operating state of the heat engine 1, in which the check valves 20 are opened cyclically for a half-stroke period in each case.
• the ratio of cylinder-piston units 2-5 in the heating phase to cylinder-piston units 2-5 in the cooling phase here is 2: 2, which means approximately equal warm-up and cool-down phases, e.g. because of reduced heat, takes into account.
• control device 20 is in the third operating state of Fig. 2c, in which the ratio of cylinder piston units 2 - 5 in the heating phase to cylinder piston units 2 - 5 in the cooling phase. 3 : 1 is.
• the operating state Figure 2a, Figure 2b and Figure 2c is adjusted depending on the controller 21 by the output pressure p 2 (and optionally also dependent on the input pressure p) falls below the output pressure p 2 a predetermined lower Gren- ze p 2, min of its first range, in particular the liquefaction pressure of the expansion fluid 8 at the current operating temperature, the ratio of cylinder-piston units 2 - 5 in the heating phase to cylinder-piston units 2 - 5 is gradually increased in the cooling phase, eg 1: 3 -> 2: 2 -> 3: 1; If the output pressure p 2 exceeds a predetermined upper limit p 2 , ma x, eg the condensing pressure plus a hysteresis threshold, then this ratio is successively reduced, eg 3: 1 -> 2: 2 -> 1: 3.
• control may be extended to any number of cylinder-piston units 2-5, for example to 3, 5, 6, 7, 8, 12, 24, etc. cylinder-piston units. The more cylinder-piston units are available, the finer graduated the control can be done.
• control device 21 can additionally shorten or lengthen each individual heating or cooling phase, for example by offsetting the beginning ti of a heating phase and / or the beginning t 2 of a cooling phase or changing the duration t 2 -ti. If heating or cooling phases of different cylinder-piston units 2 - 5 overlap in a short-term manner in a ratio (1: 3, 2: 2, 3: 1) that is greater or smaller than that selected with the aid of the aforementioned primary control, can corresponding short-term pressure fluctuations of the output pressure p 2 and inlet pressure pi by means of the buffer 15 ', 15 "in the hydraulic circuit 10 - 13 are temporarily absorbed.
• control device 21 can only perform the latter fine adjustment, with a corresponding restriction regarding exploitable operating conditions.
• FIG. 3 shows a concrete realization and further development of the heat engine 1 of FIG. 1, wherein for the sake of clarity only two cylinder piston units 2, 3 are shown in place and the control device 21 with its measuring and control lines is not shown.
• a pump 23 conveys heat transfer medium 17, for example Refrigerant R 123 from Hoechst, from a supply 24 via a line 25 to the solar panel 18, from there via the line 19 and the check valves 20 to the heat exchangers 16, and There, via switching valves 26 and a return line 27 back to the reservoir 24.
• the right check valve 20 is just opened and the left check valve 20 is closed, so that the right cylinder-piston unit 3 in the heating and Expansion phase and the left cylinder-piston unit 2 is in the cooling and contraction phase.
• the heat supply device 16-20 also comprises a device for forced cooling of the expansion fluids 8.
• the forced cooling device may be, for example, an optional feed path 28 for non-heated heat transfer medium 17, in order to provide it as shut-off valves 20 designed as a multi-way valve in the cooling phases in FIG to feed the heat exchanger 16.
• separate heat exchangers could be used for a separate cooling medium (not shown).
• the forced cooling device preferably comprises a controllable pressure relief device which, after closing the shutoff valve 20, relaxes the heat transfer medium 17 which is still under the delivery pressure of the pump 23 via the switching valve 26 to a negative pressure intermediate store 29.
• the negative pressure in the vacuum buffer 29 is established via a suction line 30 from a Venturi -Ej ector 31 which is continuously fed via a line 32 by the pump 23 with heat transfer medium 17 in a circle. Due to the sudden expansion of the heat transfer medium 17 after the opening of the switching valve 26, the heat transfer medium 17 evaporates and thereby cools the expansion fluid 8 via the heat exchanger 16.
• FIGS. 4a and 4b each show a further embodiment of a forced cooling device for the expansion fluids 8, which can be used alternatively or in addition to the aforementioned forced cooling device.
• the forced cooling device of FIGS. 4a and 4b is in each case integrated directly into one of the cylinder-piston units 2-5, and FIGS. 4a and 4b respectively show, by way of example, a cylinder-piston unit 2 equipped in this way.
• the cylinder-piston unit 2 is assembled with an auxiliary-cylinder-piston unit 40 which has a cylinder 41 and a piston 42.
• the piston 42 of the auxiliary cylinder-piston unit 41 is mechanically driven e.g. driven by a piston rod 43 of the piston movement of the cylinder-piston unit 2.
• the cylinders 6 and 41 may be assembled together axially next to each other.
• a container 44 containing an evaporation means 45 which is in the operating position shown, for example up to a level 45 'liquid and above gaseous.
• the interior of the container 44 is connected via a - formed here in the interior of the piston rod 43 - flow connection 46 with a cylinder chamber 47 of the auxiliary cylinder-piston unit 40 in flow communication.
• the opposite cylinder space 48 of the auxiliary cylinder-piston unit 40 is initially empty in the operating position shown in FIG. during the upward movement of the piston 42 is formed in the space 48 increasing negative pressure or - as far as the piston seals allow - vacuum.
• the two chambers 47 and 48 on both sides of the piston 42 of the auxiliary cylinder-piston unit 40 are connected to one another via one or more check valves 49 in fluid communication.
• the check valves 49 are oriented to progressively compress the piston 42 as the negative pressure in the space 48 increases and the evaporation means 45 in the space 47, in the flow connection 46, and in the reservoir 44 progressively compresses is closed.
• the expansion fluid 8 expands, the evaporation means 45 is thus compressed and progressively liquefied as the level 45 'rises while at the same time releasing negative pressure in the space 48.
• Piston 42 controlled, u.zw. Forcibly open in their reverse direction when the piston 42 reaches its upper setting. For example, they are pushed open by corresponding pins or levers with which they strike against the inner end face of the cylinder 41. As a result, they are opened and the compressed, pressurized evaporation means 45 relaxes abruptly in the vacuum of the space 48, see arrows 50, whereby the evaporation means 45 abruptly cools. Through the heat-conductive connection of the container 44 to the expansion fluid 8 so that this is cooled abruptly and thus supports the cooling of the expansion fluid 8 and the retraction movement of the piston 7 and accelerated.
• the check valves 49 open in their forward direction, so that the evaporation agent 45 is again displaced from the space 48 in the space 47, in the flow connection 46 and in the container 44.
• the check valves 49 close again and the process starts again.
• the compression, sudden relaxation (evaporation) and recompression of the evaporation agent 45 is a self-contained, closed cycle process, which positively supports the temperature circulation of the expansion fluid 8.
• FIG. 4b differs from that of FIG. 4a in that the auxiliary cylinder-piston unit 40 has only one effective cylinder space 48, whereas the cylinder space 47 is open or unused, or eg additionally with a coolant (not shown) can be acted upon.
• the container 44 is here via the flow connection 46 and a deflection 46 'thereof in the piston 42 directly to the Cylinder chamber 48 in flow communication, wherein the check valve 49 in the flow connection 46, for example, the deflection 46 'acts, in the same manner as in Fig.
• auxiliary cylinder-piston unit 40 or the components required for this cyclic process could also be constructed separately from the cylinder-piston unit 2 and coupled to it via corresponding flow connections and mechanical couplings.
• a larger number of cylinder-piston units could also be controlled in groups in groups in the same speed in order to control the circuit and control reducing effort;
• the cylinders 6 of a synchronizing group of cylinder-piston units could also share a common heat exchanger 16 and / or a common expansion fluid 8.

Landscapes

• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical Kinetics & Catalysis (AREA)
• Engine Equipment That Uses Special Cycles (AREA)
• Lubrication Of Internal Combustion Engines (AREA)

Priority Applications (1)

Applications Claiming Priority (2)

Publications (2)

Family

ID=45606883

Family Applications (1)

Country Status (5)

Families Citing this family (4)

Family Cites Families (6)

• 2011
  • 2011-01-28 AT ATA117/2011A patent/AT510434B1/de not_active IP Right Cessation
• 2012
  • 2012-01-05 EP EP12703950.1A patent/EP2668374B1/fr active Active
  • 2012-01-05 PL PL12703950T patent/PL2668374T3/pl unknown
  • 2012-01-05 WO PCT/AT2012/050001 patent/WO2012100275A2/fr active Application Filing
  • 2012-01-05 ES ES12703950.1T patent/ES2551397T3/es active Active

Non-Patent Citations (1)

Also Published As

Similar Documents

Legal Events