EP3101257A1 - Heat transfer unit and methods for performing thermodynamic cycles by means of a heat transfer unit - Google Patents

Abstract

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 trochoid and Zweieck flask. The solution according to the invention is an arrangement of two identical rotary piston machines (KKM) and one 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 cycle processes with external heat or heat dissipation without the use of Valve control leads. The assembly shares in a process-phased manner the shared working medium into a subset of compression and a subset of expansion. Hereinafter, the term "heat transfer aggregate" (WTA) is used for the entire aggregate.

Description

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.

The prior art is disclosed in the following patent publications.

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. As a result, 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 4179890 A and US 5211017 A have as a common feature completed media cycles, however, these units do not work with double-sided pistons. From a thermodynamic point of view, this results in other, less favorable process conditions, since geometrically only small pressure changes can be realized. The media change over channels in the raceway surfaces can lead to short-circuit flow around the pistons.

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.

Presentation of the invention

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 Kreisprozessführung 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. Hereinafter, the term "heat transfer aggregate" (WTA) is used for the entire 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. 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. This only leads to a satisfactory solution when the piston after the in WO 2008065017 A1 have been established operating principle and meet the demand for an active, acting with spring or media forces, surface seal. According to the Coulomb friction law, the frictional forces do not depend on the size of the friction surfaces. The radial seals at the tips of the pistons are made by resilient sealing strips, which at the same time invest resiliently in the axial direction of the side cover and thus provide a complete seal of the working chambers against each other. This sealing system is the known state of the art and internationally protected by patent assignments. It is not the subject of the present application, however, the sealing surface area of the piston sides on the side covers is a necessary requirement of the inventive solution. Two co-operating same rotary engines with einbogiger Trochoide in turn only result in a largest change in volume of the media subsets when the Trochoids have the same orientation with respect to their major axis and when their pistons offset by 90 degrees. According to the invention for this purpose, a total of four openings in the side covers (one opening in each side cover) 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. In each case 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. On the common shaft, an electrodynamic unit (EDE) is arranged on one side. In each case, there are two openings of a rotary piston machine, seen diagonally opposite at an angle of 45 degrees to an imaginary main axis of the single-arched trochoid. The arrangement of all openings of both rotary engines is, seen schematically, a cross with two offset by 90 degrees axes.

At a working position of the first delta-piston at an angle of 45 degrees and the second delta-piston at an angle of -45 degrees to the imaginary major axis of the single-arched trochoid are all openings in the side covers through the piston tips for the change of the working medium between the Closed-circuit engines closed.

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.

In one embodiment, a connecting line with a valve for pressure equalization during filling, starting or stopping of the unit is arranged between the connecting channels.

In a further embodiment, 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. In a hermetically sealed pressure system, 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.

Embodiment of the invention

• Figuren 1a bis 2d einen Durchlauf des thermodynamischen Prozesses mit den verschiedenen Stellungen der Kolben,
• Figuren 2a bis 2d einen Durchlauf des thermodynamischen Prozesses mit eingezeichneten rohrförmigen Kanälen,
• Figuren 3a bis 3f in einer Abfolge von Schritten den Zusammenbau des Aggregats mit Seitendeckeln entlang einer gemeinsamen Achse,
• Figur 4a einen Längsschnitt durch die erfindungsgemäße Vorrichtung,
• Figuren 4b und 4c die angeschlossenen rohrförmigen Kanäle in verschiedenen Rotationsansichten des Wärme-Transfer-Aggregats,
• Figur 5 die Stellung der Kolben mit gleich großen Arbeitsvolumina mit einem Ventil für einen Druckausgleich und
• Figur 6 ein weiteres Ausführungsbeispiel zur Steigerung der Leistung.

The principal function of the device according to the invention will be described by way of example. To show the

• FIGS. 1a to 2d a passage of the thermodynamic process with the different positions of the pistons,
• FIGS. 2a to 2d a passage of the thermodynamic process with drawn tubular channels,
• FIGS. 3a to 3f in a sequence of steps, assembling the aggregate with side covers along a common axis,
• FIG. 4a a longitudinal section through the device according to the invention,
• Figures 4b and 4c the connected tubular channels in different rotational views of the heat transfer unit,
• FIG. 5 the position of the piston with equal working volumes with a valve for pressure equalization and
• FIG. 6 another embodiment for increasing the performance.

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. On the common shaft an electrodynamic unit EDE is arranged on one side. 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.

In 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. In the housing of the rotary piston engine KKM1 on the shaft 3 a double-headed piston 2a runs with the markings of its tips with A1 and B1. Likewise, 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. In the housing of the rotary piston engine KKM2 on the shaft 3 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. 1a to 1d and 2a to 2d , Both KKM1 and KKM2 rotary engines are equivalent in their function in the WTA and interchangeable. Also disposed on the shaft 3 and connected to the side cover 6d is the electrodynamic unit EDE with a pressure housing 9 with a lateral end cover 12. In the pressure housing 9, 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.

In the Figures 4b and 4c are shown in various rotational views of the WTA. 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. These are, as in the FIGS. 1 and 3 can be seen, provided for the 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. As a result, 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. For the 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.

The functional sequence of the heat transfer unit is explained in more detail with the help of the following pictures. The 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. In this position, 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. 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". Only as a result of the start-up process do the media subsets converge. Due to unavoidable internal leakage to the otherwise sealing piston 2a, 2b, the working volumes are then mutually compensating thus a fluctuation. Figure 1c and FIG. 5 show the position of the piston 2a, 2b with equal working volumes. 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.

The Figures 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.

In the 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. Similarly, 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. Similarly, the arrangement of the opening 8b top left and the opening 7b right below diagonally opposite. This results in an arrangement pattern which, viewed from the electrodynamic unit EDE in the direction of the common axis and assuming that the side covers of both rotary piston machines KKM1 and KKM2 directly superimposed, results in a cross with two offset by 90 degrees axes in a Position of 45 degrees or -45 degrees to an imaginary major axis of the einbogigen trochoid are offset. 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. By this arrangement, the pistons 2a and 2b, both the displacement body for the thermodynamic working process and the active, by means of spring or media forces against the side surfaces sealingly acting control members for opening and closing the openings 7a, 7b, 8a and 8b for the change of Working medium between the rotary piston engines KKM1 and KKM2 in the thermodynamic working process.

The 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. As a result, two working chambers are connected to a common working volume.

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.

The 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. In the 45 degree positions of the pistons 2a and 2b ( Fig. 2a and 2d ), the connecting channels 4 and 5 are closed by the side surfaces of the piston.

The 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. In the side cover 6b is the opening 7a, in the side cover 6c, the opening 7b. To the openings 7a and 7b of the not shown in this figure tubular connecting channel 4 connects.

Out 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. In the shown Piston position after the 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.

In Figure 3c the second side cover 6d is added to the rotary piston machine KKM2 with the opening 8b. In the piston position after the FIGS. 1a and 2a Also, the opening 8b is closed by the piston 2b. To the openings 8a and 8b of the not shown in this figure tubular connecting channel 5 connects.

In 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. Here are clearly seen the openings 8a in the side cover 6a and the opening 7a in the side cover 6b of the rotary piston machine KKM1 and the opening 7b in the side cover 6c and the opening 8b in the side cover 6d of the rotary piston machine KKM2. 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. Thus, the connecting channel 5 is also closed in this piston position.

The operation of the unit is explained below. This is done on the basis of FIGS. 2a to 2d , In the piston position to FIG. 2a the aggregate has the minimum working volume "above" the pistons 2a and 2b, the pistons are rotated 45 degrees from the main axis in the direction of the flattened sides of the single-arched trochoid. The working chambers above the piston are connected by the connecting channel 4 and form a common working volume. "Below" the piston 2a and 2b, the unit has the maximum working volume. The working chambers below the pistons 2a and 2b are connected by the connecting channel 5 and also form a common working volume. Upon rotation of the pistons 2a and 2b, the upper working volume increases, the lower Work volume is reduced. The volume changes are the actual functionality of the heat transfer unit.

A characteristic important to the 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: In piston rotation, besides the change in working volumes, 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. If the pattern of arrangement of the apertures in the side covers is rotated from the 45 degree / 135 degree orientation, the effect of intense heat transfer is lost. The heat transfer at the connection channels 4 and 5, however, are of importance for the WTA since there is no metabolism with the environment.

First, 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. In the upper working volume 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. At the same time, in the lower working volume, there is an 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 effect of the flow reversal takes place with the same phase position and for the same reasons also with the lower working volume.

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.

Considered is a left-handed thermodynamic work machine cycle. For this operating variant, the energy is supplied via the electrodynamic unit EDE, which operates here as a drive motor. Starting with a position of the piston 2a and 2b after FIG. 2a isochore in the lower working volume an increase in pressure of the working medium up to a rotation angle of about 30 degrees, FIGS. 2b . 2c and 2d ,

To FIG. 2a the compression of the working medium, for example CO2 as a refrigerant, 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.

At the same time in the upper working volume isochronous release of heat energy to an ambient space, connected to a pressure reduction of the working medium. This pressure reduction corresponds to the throttle relaxation in conventional refrigeration circuits. In the case of the described unit, however, the pressure reduction is a recovery of mechanical energy, which is given as torque to the shaft 3 and represents a discharge of the drive of the electrodynamic unit EDE. The further expansion of the working medium in the upper working volume takes place as Polytrope. It takes place via the connecting channel 4, the further release of heat energy to the ambient space with further cooling, wherein it gives off mechanical work on the rotation of the piston 2 a and 2 b to the shaft 3.

Figure 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.

Considered is another right-handed thermodynamic engine cycle.

The described hermetic encapsulation of the unit allows further operating variants. Thus, with the illustrated basic geometry of two rotary engines with einbogiger trochoid in real design pressure change values between minimum and maximum volume of the media subsets can reach up to a value of about 6. In connection with a basic filling pressure of the unit of, for example, 300 bar, which corresponds technically only average requirements, pressures in the upper working volume of about 1800 bar can be achieved.

For all internal rotating components of the encapsulated heat transfer unit WTA, these pressures do not imply any additional requirement in terms of strength. However, the outer components of the enclosure must meet these requirements. For certain inert working media such as CO2, however, these pressures mean that they are "to the left" of their inversion line. This changes their material properties. During compression, they cool down, with expansion, a warming occurs.

If 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. When 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.

If one considers the environment of the heat transfer aggregate and the heat transfer aggregate as an overall system, the energy balance results in that all supplied and discharged energy quantities are in equilibrium. 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. The 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.

In FIG. 6 In a further embodiment, an arrangement is shown, which contributes to the increase of the power. For this purpose, a heat pipe 15 is arranged between the connecting channel 4 and the connecting channel 5. On the connection channel 4, 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. At the connecting channel 5 15 heat is dissipated by the heat pipe, which supports the cooling, and the connection channel 4 is Heat is supplied, which either supports the heat input into the heat transfer unit (Stirling) or goes into the heat dissipation (cooling process).

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.

reference numeral

KKM1

first rotary engine

KKM2

second rotary engine

EDE

electrodynamic unit

WTA

Heat transfer unit

1a

Housing of the KKM1

1b

Housing of the KKM2

2a

Double-headed piston of the KKM1

A1, B1

Tips of the delta-piston 2a

2 B

Double-piston KKM2

A2, B2

Tips of the delta-piston 2b

3

wave

4

connecting channel

41

Connection for the heat pipe 15 to the connection channel 4

5

connecting channel

51

Connection for the heat pipe 15 to the connection channel 5

6a

left side cover of the KKM1

6b

right side cover of the KKM1

6c

Left side cover of the KKM2

6d

right side cover of the KKM2

7a

Opening in the side cover 6b

7b

Opening in the side cover 6c

8a

Opening in the side cover 6a

8b

Opening in the side cover 6d

9

Pressure housing of the electrodynamic unit EDE

10

stator

11

rotor

12

lateral end cover

13

pressure-tight end cover

14

Valve

15

heat pipe

31a

Eccentric (KKM1)

31b

Eccentric (KKM2)

Claims (13)

Heat transfer unit consisting of two mutually connected via connecting channels (4, 5) and a common shaft (3) rotary piston machines (KKM1, KKM2) with einbogigen trochoidal and offset by 90 degrees against each other two-piston (2a, 2b), each with two Piston tips (A1, B1, A2, B2), wherein the connecting channels (4, 5) via four openings (7a, 7b, 8a, 8b) in four side covers (6a, 6b, 6c, 6d) of the rotary piston engines (KKM1, KKM2) allow a change of the working medium, characterized in that
in each case only one opening (7a, 7b, 8a, 8b) in each case one side cover (6a, 6b, 6c, 6d) is arranged in such a way that the passing piston tips (A1, B1, A2, B2) as control means for opening and closing the openings (7a, 7b, 8a, 8b) for the change of working fluid between the rotary piston engines (KKM1, KKM2) in the thermodynamic working process sealingly, and that an electrodynamic unit (EDE) on one side of the common shaft (3) is. Heat transfer unit according to claim 1, characterized in that in each case two openings (7a, 8a; 7b, 8b) of a rotary piston engine (KKM1; KKM2) are seen diagonally at an angle of 45 degrees to an imaginary main axis of the single-arched trochoid lie opposite and the arrangement of all openings (7a, 8a, 7b, 8b) of both rotary piston machines (KKM1, KKM2) are arranged as a schematically seen cross with two axes offset by 90 degrees. Heat transfer unit according to claim 1 or 2, characterized in that
at a working position of the first delta-piston (2a) at an angle of 45 degrees and the second delta-piston (2b) at an angle of -45 degrees to the imaginary major axis of the single-arched trochoid all openings (7a, 7b, 8a, 8b ) in the side covers (6a, 6b, 6c, 6d) through the Piston tips (A1, B1, A2, B2) for the change of the working medium between the rotary piston engines (KKM1, KKM2) are closed. Heat transfer unit according to claim 1, characterized in that the connecting channel (4) between the opening (7a) of the inner side cover (6b) of the rotary piston machines (KKM1) to the opening (7b) of the inner side cover (6c) of the two rotary piston engines ( KKM2) and the connecting channel (5) from the opening (8a) of the outer side cover (6a) of the rotary piston engine (KKM1) to the opening (8b) of the outer side cover (6d) of the rotary piston engine (KKM2) are arranged. Heat transfer unit according to claim 1 or 4, characterized in that
the connecting channels (4, 5) are tubular. Heat transfer unit according to claim 1, 4 or 5, characterized in that
the connecting channels (4, 5) are connected to heat exchangers. Heat transfer unit according to claim 1, 4, 5 or 6, characterized in that
between the connecting channels (4, 5) a connecting line with a valve (14) for pressure equalization during filling, starting or stopping the unit is arranged. Heat transfer unit according to claim 1, 4, 5 or 6, characterized in that
between the connecting channel (5) and the connecting channel (4) a heat pipe (15) is arranged, which supports a dissipation of heat at the connecting channel (5) and a supply of heat at the connecting channel (4). Heat transfer unit according to one of the preceding claims 1 to 8
characterized in that
it is constructed as a hermetically sealed pressure system, in all individual housing parts of the two rotary piston engines (KKM1, KKM2) and the electrodynamic unit (EDE) itself are part of a common hermetic encapsulation. Method for carrying out thermodynamic cycle processes by means of a heat transfer unit using two mutually connected via a common shaft (3) rotary piston machines (KKM1, KKM2) with einbogigen trochoidal and offset by 90 degrees against each other two-piston (2a, 2b) characterized in that, in a hermetically sealed pressure system, each of the rotary engines (KKM1, KKM2) uses, by itself, and by mechanical coupling and expansion, a closed working medium circulating in both rotary engines (KKM1, KKM2) to heat energy between heat sources and heat sinks, which constitute a heat source heat sink system and are in communication with the heat transfer unit, and transfer an amount of energy resulting from the transfer process by an electrody connected to the rotary engines (KKM1, KKM2) via the common shaft (3) Namely unit (EDE) removes or supplies the heat source heat sink system. A method according to claim 10, characterized in that the working medium circulates between the rotary piston engines (KKM1, KKM2) with varying pressures to a mean pressure of the hermetically sealed pressure system. A method according to claim 10, characterized in that the electrodynamic unit (EDE) operates as a motor, generator or starter generator. A method according to claim 10, characterized in that between two rotary piston machines (KKM1, KKM2) arranged connection channels (4, 5) via a heat pipe (15) exchange heat in the Type, that the connecting channel (5) dissipates heat and the connecting channel (4) heat is supplied.

Images