EP3101257A1 - Groupe de transfert thermique et procédé d'exécution d'un processus circulatoire thermodynamique à l'aide d'un groupe de transfert thermique - Google Patents

Groupe de transfert thermique et procédé d'exécution d'un processus circulatoire thermodynamique à l'aide d'un groupe de transfert thermique Download PDF

Info

Publication number
EP3101257A1
EP3101257A1 EP15170474.9A EP15170474A EP3101257A1 EP 3101257 A1 EP3101257 A1 EP 3101257A1 EP 15170474 A EP15170474 A EP 15170474A EP 3101257 A1 EP3101257 A1 EP 3101257A1
Authority
EP
European Patent Office
Prior art keywords
heat
kkm1
kkm2
piston
heat transfer
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Withdrawn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
EP15170474.9A
Other languages
German (de)
English (en)
Inventor
Eggert GÜNTHER
Norbert GÜNTHER
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.)
EN3 GmbH
Original Assignee
EN3 GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by EN3 GmbH filed Critical EN3 GmbH
Priority to EP15170474.9A priority Critical patent/EP3101257A1/fr
Publication of EP3101257A1 publication Critical patent/EP3101257A1/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/22—Rotary-piston machines or engines of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth- equivalents than the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • 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
    • F02G2270/00—Constructional features
    • F02G2270/10—Rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/14—Power generation using energy from the expansion of the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the invention relates to a heat transfer unit and a method for carrying out thermodynamic cycle processes by means of a heat transfer unit using two interconnected rotary piston engines with einbogigen trochoidal and delta-piston.
  • US 5335497 A has two common-shaft twin-piston pistons that use a closed working fluid for compression and expansion.
  • the change of media to / from the workspaces takes place via the raceway surfaces.
  • both pistons have a short-circuit flow at certain angular positions.
  • the described thermodynamic process sequence is not feasible with the illustrated angular positions piston without additional control elements.
  • US 5317996 A shows a machine having a plurality of connected by a common shaft Zweieck-piston.
  • the media change takes place via openings in the raceway surfaces.
  • the openings are arranged so that in certain angular positions short-circuit flows around the pistons occur, which can not be avoided by the proposed control organs.
  • EP 1075595 B1 has two triangle pistons.
  • the machine has two housings in the shape of two-bows Trochoids, according to the well-known Wankelmaschine.
  • the machine uses a common sealed working fluid with the media change channels between the housings attaching to the side covers.
  • DE 3333586 A1 shows two rotary piston machines, whose inner-axis rotors each form two working chambers by two from the outside, guided in the housings slides.
  • the rotors are eccentric to the circular housings. They are connected by a common wave.
  • the rotors have a rotation angle offset of 90 degrees.
  • the machine works with a sealed medium.
  • the change of media to / from the workspaces takes place via the raceway surfaces.
  • the arrangement of the sealing elements in the form of the slide contradicts the Wankeischen axiom, according to which a functioning rotary piston machine may only have two relatively moving, forming the working space components and the sealing elements must be arranged on the moving component.
  • the object of the invention is to carry out the realization of a heat transfer unit under the basic principles of thermodynamic processes such as a Stirling process or a CO2 refrigeration process, wherein a Kreisreament completed media with sufficient pressure changes between compression and Expansion and a hermetic completion of the heat transfer unit are required to allow processes under higher pressures can.
  • a Guaranteereament completed media with sufficient pressure changes between compression and Expansion and a hermetic completion of the heat transfer unit are required to allow processes under higher pressures can.
  • Higher pressures and thus higher substance densities of the closed media result in better heat transfer values between the circulating medium and the components through which the medium flows and increase the power density of the cycle or the arrangement.
  • the solution of the problem is realized by the arrangement of two identical rotary piston machines (KKM) and an electrodynamic unit (EDE), which are located in a hermetic system.
  • the two rotary piston engines are connected within the hermetic system by a common real or functional shaft, wherein their rotary motion is a common closed, in mass and total volume constant working medium through the process phases compression and expansion in thermodynamic cycles with external heat or heat dissipation without the use of Valve control leads.
  • the assembly divides the shared working medium into a subset of compression and a subset of expansion in a process-phased manner.
  • WTA heat transfer aggregate
  • the inventive solution is based on the requirement profile derived from the analysis of the prior art.
  • This requirement profile involves the use of two identical rotary piston machines (RKMs), which satisfy the condition that they fulfill the Wanke's axiom, according to which only machines function as prime movers consisting of only two components moving relative to each other and bounding the working space.
  • RKMs rotary piston machines
  • Part of the requirement profile is that of all the machines considered below, only two identical rotary piston engines (CCM) with a double-sided piston and a single-bore trochoid are used. They show the largest volume changes in the process phases.
  • Geometrically conditioned and characteristic of Zweieck-Kolben is the possibility of Short-circuit flow around the piston, if openings for changing the media of a KKM are not arranged exactly diametrically to the longitudinal axis of the piston and are not divided in the circumferential direction by the piston tips. It follows that the openings for the media change must not be arranged in the tread contour of the single-arched trochoid, as this leads to short-circuit flows around the delta-piston and thus to cancel the delimitation of the media subsets.
  • the openings for the media change are to be arranged in the side covers, as it already is EP 1075595 B1 is apparent.
  • the pistons of the KKM are also the control organs for opening and closing the openings.
  • a total of four openings in the side covers may be arranged, which have a pattern arrangement, which results in a view in the direction of the common axis a cross with two offset by 90 degrees axes, each opposite 45 degrees an imaginary one Main axis are offset.
  • the apertures in the side covers are arranged close to the trochoidal contours along the axes of the cross so that all the apertures can be completely and equally spaced away from the piston centers by the passing sides of the piston, thus preventing the avoidance of short circuit flow around the two-cornered pistons.
  • the heat transfer unit according to the invention consists of two mutually connected via connecting channels and a common shaft rotary engines with einbogigen trochoidal and offset by 90 degrees against each other two-piston with two piston tips.
  • the connection channels allow a change of the working medium via four openings in the four side covers of the rotary piston engines.
  • a side cover only one opening is arranged in each case such that the passing piston tips act as a control organs for opening and closing the openings for the change of the working medium between the rotary piston engines in the thermodynamic working process sealing.
  • EEE electrodynamic unit
  • a communication passage is disposed between the openings of the inner side covers of the two rotary engines, and the second communication passage is disposed between the openings of the outer side covers of both rotary engines.
  • the connection channels are tubular and connected to heat exchangers.
  • a connecting line with a valve for pressure equalization during filling, starting or stopping of the unit is arranged between the connecting channels.
  • a heat pipe is arranged between the second connection channel and the first connection channel, which supports a dissipation of heat at the second connection channel and a supply of heat at the first connection channel.
  • the method according to the invention for carrying out thermodynamic cycle processes by means of a heat transfer unit uses two rotary piston machines connected to one another via a common shaft with single-sided trochoidal and two-cornered pistons staggered by 90 degrees.
  • each of the rotary engines uses, by itself and by mechanical coupling, by mechanical compression and expansion, a closed working fluid circulating in both rotary engines.
  • Heat energy is transferred between heat sources and heat sinks which form a heat source heat sink system and communicate with the heat transfer aggregate.
  • a resulting amount of energy balancing with the transfer process is taken or supplied to the heat source heat sink system by an electrodynamic unit connected to the rotary engines via the common shaft.
  • the heat transfer unit is constructed as a hermetically sealed pressure system in which all individual housing parts of the two Rotary piston engines and the electrodynamic unit itself are part of a common hermetic encapsulation.
  • the working fluid circulates between the rotary engines at varying pressures around a mean pressure of this hermetically sealed pressure system.
  • the electrodynamic unit works as a motor, generator or starter generator.
  • the inventive device for carrying out thermodynamic cycles consists of two interconnected rotary piston engines (KKM) with einbogigen trochoid and delta-piston, which via tubular connecting channels and a common shaft together to form a heat transfer unit (WTA) are connected.
  • KM rotary piston engines
  • WTA heat transfer unit
  • EDE electrodynamic unit
  • the arrangement of the electrodynamic unit EDE on the common shaft of the unit is not to be arranged between the two interconnected rotary engines of the unit, since this arrangement increases the length of the channels between the side covers and thus brings greater dead volume in the unit. Therefore, the electrodynamic unit EDE is sealingly arranged at one end of the common shafts of the unit, outside the shaft bearing of the two rotary engines.
  • the electrodynamic unit EDE has the same pressure level of the WTA at rest, but this part of the working medium does not participate in the process-related circulation of the working medium.
  • the housings and the side covers of the rotary engines are themselves part of a common hermetic enclosure, which is completed by end covers.
  • the individual housing parts of the two rotary piston engines are at the same time parts of a hermetic pressure system.
  • FIG. 4a A longitudinal section through the device, starting from the left on the shaft 3, a first rotary piston machine KKM1, a second rotary piston machine KKM2 and the electrodynamic unit EDE are arranged.
  • the first rotary piston machine KKM1 consists of a housing 1a with a single-curved trochoid as the raceway contour, a left side cover 6a arranged outwardly and a right side cover 6b arranged towards the rotary piston machine KKM2.
  • the side cover 6a is connected to a pressure-tight end cover 13, which surrounds the shaft 3 pressure-tight.
  • a double-headed piston 2a runs with the markings of its tips with A1 and B1.
  • the second rotary piston machine KKM2 consists of a housing 1 b with a single-curved trochoid as a raceway contour and a left to the rotary piston machine KKM1 out arranged side cover 6c and a outwardly to the electrodynamic unit EDE arranged right side cover 6d.
  • a double-headed piston 2b runs with the markings of its tips with A2 and B2. The marking of the tips of the two double-sided pistons 2a and 2b with the tips A1, A2, B1 and B2 is carried out for a simpler visualization of the movement sequence of the pistons 2a and 2b in the FIGS.
  • Both KKM1 and KKM2 rotary engines are equivalent in their function in the WTA and interchangeable.
  • the electrodynamic unit EDE with a pressure housing 9 with a lateral end cover 12.
  • a rotor 11 is arranged on the shaft 3, which is surrounded by a stator 10.
  • the hermetic encapsulation of the WTA must not be interrupted by the passage of a rotating shaft 3.
  • a non-illustrated pressure-tight passage through the pressure housing 9 is provided for cast in the capsule electrical cables.
  • FIGS. 1 and 3 show a tubular connecting channel 5 (FIG. Fig. 4b ) runs from the left side cover 6a of the rotary piston engine KKM1 to the right side cover 6d of the rotary piston engine KKM2 on the outside around both rotary piston machines KKM1 and KKM2 on the "cold" working side of the heat transfer unit.
  • FIGS. 1 and 3 show a tubular connecting channel 5 in the side cover 6a an opening 8a and in the side cover 6d an opening 8b.
  • Figure 4c shows a rotated by approximately 180 degrees view, so that the electrodynamic unit EDE is now located on the left side.
  • a tubular connecting channel 4 between the right side cover 6b of the rotary piston engine KKM1 and the left side cover 6c of the rotary piston engine KKM2 is visible on the "hot" working side of the heat transfer unit.
  • Connecting channel 4 are in the side cover 6b an opening 7a and in the side cover 6c an opening 7b provided.
  • the arrangement of the tubular connection channels 4 and 5 between the openings 7a, 7b, 8a and 8b in the side covers is such that the connection channel 4 between the two inner side covers 6b and 6c between the two rotary piston machines KKM1 and KKM2 and the connecting channel 5 from the outer Side cover 6a to the other outer side cover 6d of the unit runs.
  • Each of the four side covers 6a to 6d of the unit has only one opening for the change of the working medium.
  • the openings 7a, 7b, 8a and 8b are located in the area of the passing lateral piston tips A1, A2, B1 and B2.
  • FIGS. 1a to 2d show a passage of the thermodynamic process with the various positions of the piston, the rotary piston machines KKM1 and KKM2 are in the drawing plane next to each other, although in the real aggregate, the rotary piston machines KKM1 and KKM2 are superimposed with respect to the plane of the drawing. This is necessary for reasons of clear representation of the functional relationships, from this there is no impairment in the presentation of the inventive request.
  • FIG. 1a shows the position of the piston 2a of the rotary piston machine KKM1 directed at an angle of 45 degrees to the main axis of the single-arched trochoid.
  • the main axis defines a line passing through the mathematical origin of the trochoid and the center of the wave 3.
  • the piston tip B1 is at the top and the piston tip A1 is at the bottom.
  • a smaller working chamber is located on the left above the piston 2a and a larger working chamber on the right below the piston 2a.
  • the position of the piston 2b of the rotary piston engine KKM2 is directed at an angle of 135 degrees to the main axis.
  • the piston tip A2 is at the top and the piston tip B2 is at the bottom.
  • a smaller working chamber is located on the right above the piston 2b and a larger one Working chamber on the left below the piston 2b.
  • the pistons 2a and 2b are formed with the working chambers of the rotary piston engines KKM1 and KKM2 working volumes by the two smaller working chambers are communicatively connected through the tubular connecting channel 4 and the two larger working chambers through the tubular connecting channel 5.
  • the two smaller connected working chambers give the minimum, the two larger working chambers give the maximum working volume of the WTA.
  • the heat transfer unit WTA At rest, the heat transfer unit WTA have the media subsets in the two working volumes the same pressure level, regardless of the piston positions, since their mutual sealing by the piston 2a, 2b is only "dynamically tight".
  • FIG. 5 shows in one embodiment, a valve 14 in a connecting line, with the between the connecting channels 4 and 5, the pressure compensation for filling, starting and stopping the unit can be done.
  • FIGS. 1b and 1c show the position of the piston 2a and 2b after a rotation of 45 degrees clockwise.
  • Figure 1d shows the position of the pistons 2a and 2b after a total rotation of 180 degrees clockwise.
  • the heat transfer unit has again reached the minimum or maximum working volume.
  • the marked piston tips A1 and B1 or A2 and B2 are now cyclically reversed by the piston tip A1 above and the piston tip B1 below and the piston tip B2 above and the piston tip A2 are down.
  • FIGS. 1a to 1d are the opening 8a in the side cover 6a, the opening 8b in the side cover 6d (in the outer side covers 6a and 6d of the composite of the two rotary engines KKM1 and KKM2), the Opening 7a in the side cover 6b and the opening 7b in the side cover 6c (in the two inner side covers 6b and 6c of the composite of the two rotary piston machines KKM1 and KKM2) schematically drawn.
  • the opening 7a and the opening 8b are arranged below the flattened Trochoidenkontur.
  • the openings 8a and 7b point towards the circular side of the trochoid.
  • the opening 7a on the top right and the opening 8a on the bottom left of the rotary piston machines KKM1 lie, diagrammatically, diagonally opposite.
  • Each opening 7a, 7b, 8a and 8b is covered by a piston tip A1, A2, B1 and B2 when the pistons 2a and 2b are offset by 90 degrees.
  • the openings 7a, 7b, 8a and 8b covered by the lateral piston tips A1, A2, B1 and B2 are located on respectively opposite sides of the pistons 2a and 2b of a rotary piston engine KKM1 or KKM2.
  • FIGS. 2a to 2d show a passage of the thermodynamic process with marked tubular connecting channels 4 and 5 and how they are connected to the working chambers, wherein the Connecting channel 4 is disposed between the opening 7a and the opening 7b and the connecting channel 5 between the opening 8a and the opening 8b.
  • the Connecting channel 4 is disposed between the opening 7a and the opening 7b and the connecting channel 5 between the opening 8a and the opening 8b.
  • FIG. 2a shows the pistons 2a and 2b in a position corresponding to the position in FIG. 1a equivalent.
  • the connecting channel 4 connects the rotary piston engine KKM1 with the rotary piston engine KKM2.
  • the collective work volume formed hereby has its minimum in this position.
  • the connecting channel 5 also connects the rotary piston engine KKM1 with the rotary piston engine KKM2.
  • the joint working volume formed hereby has its maximum in this position.
  • FIGS. 2b to 2d show the changes in the working volumes until they have reached the respective size changes after a total rotation of the pistons 180 degrees.
  • the connecting channels 4 and 5 are closed by the side surfaces of the piston.
  • FIGS. 3a to 3f show, as a sequence of steps, the assembly of the unit with the side covers 6a to 6d along the common shaft 3.
  • FIG. 3a starts with the eccentric 31a, the side cover 6b, which belongs to the rotary piston machine KKM1, a shaft bearing, not further designated, the side cover 6c, which belongs to the rotary piston machine KKM2, and the eccentric 31b.
  • the side cover 6b is the opening 7a, in the side cover 6c, the opening 7b.
  • tubular connecting channel 4 connects to the openings 7a and 7b of the not shown in this figure.
  • FIG. 3a It can be seen that the opening 7a is offset by an angle of 45 degrees with respect to the main axis and the opening 7b by an angle of 135 degrees with respect to the main axis.
  • FIGS. 1a and 2a Both openings and thus the connecting channel 4 are closed by the piston 2a and 2b.
  • Figure 3b shows this with the piston 2b, which closes the opening 7b.
  • FIG. 3d figure also the piston 2a and the side cover 6a of the rotary piston engine KKM1 is added.
  • the FIG. 3e shows a view without a piston.
  • FIG. 3f again shows a view with two pistons 2a and 2b in the position after the FIGS. 1a and 2a , The opening 8a is closed by the piston 2a and the opening 8b is closed by the piston 2b.
  • the connecting channel 5 is also closed in this piston position.
  • thermodynamic cycles of the WTA is associated with the stated location of the openings in the side covers according to a 45 degree / 135 degree arrangement pattern:
  • the gradient of change in the individual working chambers is also important. After that, for example, when the minimum volume is increased, first a flow through the connecting channel 4 to the enlarging working chamber takes place - which is plausible. From a certain piston rotation angle, however, the gradient of the volume change in the working chamber to be filled is smaller than the gradient of the delivering chamber. This results in a reversal of the flow, resulting in an intense heat transfer in the connecting channel 4. The same effect occurs analogously on the side of reduction of the maximum volume in the connecting channel 5.
  • connection channels 4 and 5 are of importance for the WTA since there is no metabolism with the environment.
  • thermodynamic engine cycle a so-called right - handed thermodynamic engine cycle is considered. If heat energy is supplied to the connection channel 4 from an external heat source, an increase in pressure of the enclosed medium, for example helium as a heat carrier, is produced in the upper working volume, connected to pressure forces on the pistons 2a and 2b and a torque acting in the shaft 3, which is the rotation of the electrodynamic Unit EDE and output of electrical energy affects.
  • isochore pressure increase up to a rotation angle change of about 30 degrees, then the expansion of the working medium takes place with simultaneous heat supply close to one Isotherms.
  • there isochronous pressure reduction with temperature reduction in phase with the volume flow in the upper working volume.
  • This pressure reduction affects the gain of the torque in the shaft 3. Thereafter, a compression of the working medium with the release of heat energy via the connecting channel 5 to the environment. Depending on whether this heat release during compression is supported by an active cooling, this runs along a polytropic, ideally along an isotherm.
  • the unit works as an engine, similar to the Stirling engine.
  • the structural design of the unit is such that the "zero position" is preferably characterized by the 45-degree position of the piston 2a and 2b. This position causes the operation of the unit the effect that the heat transfer of an external heat energy through the wall of the connecting channel 4 is particularly intense. This effect arises from the fact that the flow of the working medium through the connecting channel 4 again reverses when the gradient of the volume change of the upper working chamber of the rotary piston engine KKM1 is greater than the gradient of the volume change of the upper working chamber of the rotary piston engine KKM2, although the two pistons 2a and Turn 2b evenly in working direction.
  • the energy balance for the unit shows that the amounts of energy supplied and discharged are in energetic equilibrium at the connection channels 4 and 5 as well as at the electrodynamic unit EDE, which works as a generator.
  • thermodynamic unit EDE which operates here as a drive motor.
  • the compression of the working medium takes place in the lower working volume.
  • the working medium takes in an isochoric phase up to a rotation angle change of about 30 degrees via the connecting channel 5 heat energy from an ambient space, connected to an increase in pressure, on.
  • the subsequent further compression is done with further absorption of ambient heat as polytrope. Accordingly, the working medium circulates between the rotary piston engines KKM1 and KKM2 with changing pressures around a mean pressure of the hermetically sealed pressure system.
  • FIG. 2d shows the completed process.
  • the cooled working fluid is now in the lower working volume, where it absorbs ambient heat via the connecting channel 5 and is compressed again. The cycle begins again.
  • the energy balance for the unit shows that the amounts of energy supplied and discharged are in energetic equilibrium at the connection channels 4 and 5 as well as at the electrodynamic unit EDE, which works as a motor.
  • the unit works as a refrigeration machine. The purpose can be both a cooling process and heating process.
  • the described hermetic encapsulation of the unit allows further operating variants.
  • pressure change values between minimum and maximum volume of the media subsets can reach up to a value of about 6.
  • pressures in the upper working volume of about 1800 bar can be achieved.
  • the heat transfer unit described is operated at a base pressure of, for example, 300 bar in a cyclic process, its properties are reversed so that when the working medium is compressed in the lower working volume, cooling takes place via the connecting channel 5, ambient heat is absorbed successful expansion in the upper working volume via the connecting channel 4 is released as useful heat.
  • the electrodynamic unit EDE is operated as a starter generator, a discharge of electrical energy takes place after the engine phase in the generator mode.
  • the heat transfer unit works as an engine, but it must be started by a starter unit similar to an internal combustion engine.
  • the energy delivered by the electrodynamic unit EDE must also be used to actively dissipate the heat at the connection channel 4 in accordance with the laws of thermodynamics.
  • thermodynamic cycle analysis on the basis of the state diagrams for CO2, for example, shows that after covering all amounts of energy for internal mechanical friction and active heat supply and removal operations on the connecting channels 5 and 4, a positive amount remains on the electrodynamic unit EDE, which consists of the hermetic Encapsulation must be led out as an electrical load and then fed again as a heat equivalent of the environment.
  • FIG. 6 In a further embodiment, an arrangement is shown, which contributes to the increase of the power.
  • a heat pipe 15 is arranged between the connecting channel 4 and the connecting channel 5.
  • a connection 41 is provided for this purpose and a connection 51 for the heat pipe 15 is provided on the connection channel 5.
  • the heat pipe 15 transports heat from the connection 51 of the connection channel 5 to the connection 41 of the connection channel 4 on a small cross-sectional area and can be used in various designs, for example in the form of a heat pipe or a two-phase thermosyphon. The function is explained below.
  • the environment of the heat transfer unit consists of a heat source heat sink system with external heat sources, such as engine waste heat, and heat sinks, such as space heating. Heat energy is transferred between the heat sources and heat sinks, and a resultant amount of energy resulting from the transfer process is extracted or supplied by an EDE to the heat source heat sink system via an external energetic application.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)
EP15170474.9A 2015-06-03 2015-06-03 Groupe de transfert thermique et procédé d'exécution d'un processus circulatoire thermodynamique à l'aide d'un groupe de transfert thermique Withdrawn EP3101257A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP15170474.9A EP3101257A1 (fr) 2015-06-03 2015-06-03 Groupe de transfert thermique et procédé d'exécution d'un processus circulatoire thermodynamique à l'aide d'un groupe de transfert thermique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15170474.9A EP3101257A1 (fr) 2015-06-03 2015-06-03 Groupe de transfert thermique et procédé d'exécution d'un processus circulatoire thermodynamique à l'aide d'un groupe de transfert thermique

Publications (1)

Publication Number Publication Date
EP3101257A1 true EP3101257A1 (fr) 2016-12-07

Family

ID=53373294

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15170474.9A Withdrawn EP3101257A1 (fr) 2015-06-03 2015-06-03 Groupe de transfert thermique et procédé d'exécution d'un processus circulatoire thermodynamique à l'aide d'un groupe de transfert thermique

Country Status (1)

Country Link
EP (1) EP3101257A1 (fr)

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4179890A (en) 1978-04-04 1979-12-25 Goodwin Hanson Epitrochoidal Stirling type engine
DE3333586A1 (de) 1983-09-16 1985-04-11 Franz X. Prof. Dr.-Ing. 8000 München Eder Aussenbeheizte regenerative waerme- und arbeitsmaschine
US5211017A (en) 1990-09-19 1993-05-18 Pavo Pusic External combustion rotary engine
US5317996A (en) 1991-07-17 1994-06-07 Lansing Joseph S Self-starting multifuel rotary piston engine
US5335497A (en) 1993-02-10 1994-08-09 Macomber Bennie D Rotary Stirling cycle engine
EP1075595B1 (fr) 1998-04-25 2004-02-11 Ceres IPR Limited Ameliorations portant sur des machines a piston rotatif
WO2008065017A1 (fr) 2006-12-02 2008-06-05 Guenther Eggert Système d'étanchéité pour le piston de machines à piston rotatif
DE102007028181A1 (de) * 2007-06-20 2008-12-24 GÜNTHER, Eggert Verfahren und System zur Integration von Rotationsmaschinen zu mehrstufigen Nutzung der Brennstoffenergie in Kombiprozessen
EP2765280A2 (fr) * 2013-02-07 2014-08-13 EN3 GmbH Procédé de transformation directe d'énergie de vapeur en énergie de pression d'un fluide de transport et installation permettant de mettre en oeuvre le procédé

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4179890A (en) 1978-04-04 1979-12-25 Goodwin Hanson Epitrochoidal Stirling type engine
DE3333586A1 (de) 1983-09-16 1985-04-11 Franz X. Prof. Dr.-Ing. 8000 München Eder Aussenbeheizte regenerative waerme- und arbeitsmaschine
US5211017A (en) 1990-09-19 1993-05-18 Pavo Pusic External combustion rotary engine
US5317996A (en) 1991-07-17 1994-06-07 Lansing Joseph S Self-starting multifuel rotary piston engine
US5335497A (en) 1993-02-10 1994-08-09 Macomber Bennie D Rotary Stirling cycle engine
EP1075595B1 (fr) 1998-04-25 2004-02-11 Ceres IPR Limited Ameliorations portant sur des machines a piston rotatif
WO2008065017A1 (fr) 2006-12-02 2008-06-05 Guenther Eggert Système d'étanchéité pour le piston de machines à piston rotatif
DE102007028181A1 (de) * 2007-06-20 2008-12-24 GÜNTHER, Eggert Verfahren und System zur Integration von Rotationsmaschinen zu mehrstufigen Nutzung der Brennstoffenergie in Kombiprozessen
EP2765280A2 (fr) * 2013-02-07 2014-08-13 EN3 GmbH Procédé de transformation directe d'énergie de vapeur en énergie de pression d'un fluide de transport et installation permettant de mettre en oeuvre le procédé

Similar Documents

Publication Publication Date Title
DE102006043250B4 (de) Mehrfachzylinder-Freikolben-Stirlingmaschinen und -Wärmepumpen in Alpha-Anordnung mit abgestuften Kolben
DE112010004335B4 (de) Gamma-Typ Freikolben-Stirlingmaschinen Konfiguration
DE4333144A1 (de) Kältemittelkompressor mit hin- und herbeweglichen Kolben
EP3146190B1 (fr) Moteur stirling à double cylindre, moteur stirling à cylindre multiple et système de génération d'énergie électrique
DE2539878C2 (de) Thermodynamische Maschine mit geschlossenem Kreislauf
DE19814742C1 (de) Kreiskolben-Wärmemotor-Vorrichtung
DE60223150T2 (de) System zur konstruktion von pumpen, verdichtern und kraftmaschinen
DE4305043A1 (en) Stirling engine of double-head piston and swash plate type - has cylinder block with front and rear working gas chambers, surrounded by heat exchangers
EP3101257A1 (fr) Groupe de transfert thermique et procédé d'exécution d'un processus circulatoire thermodynamique à l'aide d'un groupe de transfert thermique
DE4424319C1 (de) Heißgasmotor
DE3239021C2 (fr)
DE3834070C2 (fr)
EP0725899B1 (fr) Compresseur a piston pour milieux gazeux
EP2419618A1 (fr) Moteur thermique
DE1601459C3 (de) Vorrichtung mit einem Heißgasmotor und einer mit ihm gekuppelten anzutreibenden Vorrichtung
DE3939779A1 (de) Verfahren und einrichtung zur umwandlung von waermeenergie in mechanische energie
DE102007054196A1 (de) Drehkolben-Stirlingmotor
DE102012109832B4 (de) Freikolbenmaschine und Doppelzylinderfreikolbenmaschine
CH373593A (de) Triebwerk mit zwei Viertakt-Kreiskolbenmotoren
DE3709014A1 (de) Stirlingmasschine mit in einem gasdichten innenraum eines gehaeuses befindlichen drehkolben
WO2002084078A1 (fr) Dispositif de moteur thermique a pistons rotatifs
DE1426976A1 (de) Umlaufwaermepumpe
DE102010013620B4 (de) Heißgasmotor mit rotierenden Segmentkolben
DE3204017A1 (de) Drehkolbenmotor
DE19633174C2 (de) Rotations-Kolben-Kraft- oder Arbeitsmaschine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20160516

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20180103