EP3032049A1 - Heatpipe engine - Google Patents

Abstract

Summary: The invention relates to a heatpipe heat engine (1) having at least one cylinder (21), at least one double collar sleeve (22) movably guided in the cylinder (21) and at least one piston (13) movably guided in the double collar sleeve (22). and a working medium (16) used in a closed thermodynamic cycle. The heat pipe heat engine (1) has at least one warm zone (18) for evaporation and at least one cold zone (9) for condensation of the working medium (16). The transfer ports (23) mounted between the hot and cold zones are equipped with the piston-in-two-collar-piston combination (22, 13) as flow control and the spring (29) for direct mechanical work, for example, for compression use increased temperature potential or for the production of electrical energy, for example, suitable with linear generator / -en.

Description

The invention relates to the conceptually claimed and thus relates to how mechanical or electrical work can be performed with heat energy in a capillary force driven heat pipe construction or alternatively a gravity driven heat pipe.

Heatpipes and heat pipes are preferably used in known forms for the transport of heat energy. The main difference of the available designs are the types with capillary structure for liquid transport, in limits also against gravity, in contrast to the gravity-driven heat pipes (also called two-phase thermosiphon) to call.

The aforementioned heat pipes or heatpipes, hereinafter generally referred to as heatpipes, invariably run in a closed thermodynamic cycle. The advantages of high specific cycle process work are used in known heat pipes in the thermodynamic cycle, depending on the operating temperature, using different fluid working media such as water, sodium, refrigerant R134a, R600a. Prerequisite for a heat transfer with heat pipes is a temperature difference between the cold and the warm zone. The aforementioned known heatpipes usually work exclusively as a heat transport means.

The prerequisite of a temperature difference is present in our environment almost in unlimited variety. Energy transfer within heatpipes is based, as is well known, on evaporation, condensation and vapor and liquid transport between the hot and cold zones. The selection of suitable materials as well as working media for heatpipe construction are regarded as state of the art.

The pressure difference necessary for the transport of the vaporous medium is based on the evaporation of the liquid medium and thus expansion on the warm and the condensation and thus volume reduction of the vaporous medium at the cold zone. This process continues in the closed system as long as there is a temperature difference between the cold and warm zones. Among other things, it is dependent on the temperature difference of the cold and warm zone, the selected working medium and thermal conductivity of used materials, especially in the area of the heat source and the heat sink. In addition to the selected working medium, there are ideally no other foreign gases in the closed system.

It is desirable to make use of this previously used only as a heat transfer process for the generation of mechanical, electrical energy or the increase of temperature levels. Ideally, in addition to the heat energy supplied no further form of energy is necessary. Today's methods for raising temperature levels are realized, for example, by supplying electric power using compressors.

State of the art

Other inventions for the conversion of thermal energy into electrical or mechanical energy are in the patents DE 10 2005 040 866 B3 and WO 2014/012586 A1 disclosed.

It is also desirable to provide a heat pipe design that can perform mechanical or electrical work over any external source of heat, that is, without internal combustion and thus emissions of environmentally harmful gases, or alternatively can achieve the elevation of temperature levels.

It is also desirable to provide the heatpipe construction as a low maintenance, ideally maintenance-free design.

It is desirable to provide at least one of the mentioned problems with at least partial relief.

The invention has for its object to provide new to the commercial application of a generic heat pipe heat engine.

The solution to this problem is claimed in an independent form. Preferred embodiments can be found in the subclaims.

The heat pipe heat engine according to the invention has at least one cylinder and at least one piston movably guided in the cylinder. Ideally, this movable piston is guided within a double collar likewise movably inserted in the cylinder. At least one warm zone is provided on the cylinder. The necessary for the thermodynamic cycle cold zone (at least one) for the condensation of the working fluid is also, at least temporarily, in the achievable for the vaporous working medium region of the heat pipe heat engine.

Preferably, the heat energy to be supplied to the system at the warm zone is provided by a layer of material, such as aluminum, having a high thermal conductivity. The same applies to the derivation of heat energy at the cold zone, the so-called heat sink. The transport zone should ideally be thermally insulated.

It is further preferred if the movably guided piston of the heat pipe heat engine according to the invention receives at least one device, such as a spring, on the cold zone side for storing mechanical energy as a bias for the return transport of the piston and the double collar. Alternatively or in combination, magnetic variants are possible in order to force the piston-double collar combination back from the cold zone in the direction of the warm zone.

It is preferred to limit the piston stroke in the region of the transport zone of the cylinder of the heat pipe heat engine by end stops. Between the upper and lower end stop for the piston-Doppelbundhülsenkombination at least one, but ideally several transfer channels for the vaporous working medium are attached. The overall height of the double collar is smaller than the distance between the inlet and outlet of the transfer channels. The piston movably guided within the double collar sleeve has in turn a lower height than the distance between the inside Edges of the double collar sleeve from a vertical point of view. The maximum total stroke of the piston-Doppelbundhülsen combination thus results from the free movement play of the double collar between the end stops added to the axial movement play of the piston within the double collar.

Preferably come for pistons and Doppelbundhülse materials with low weight, the compatibility with the working medium used, one of the operating temperature of the heat pipe heat engine selected temperature resistance and low friction and slipstick values are used. In addition to possible metallic materials, plastics, such as under the brand name "Iglidur®" from the manufacturer igus or "Vespel®" from DuPont ™, are ideal alternatives because of their good processing properties.

Furthermore, the piston and Doppelbundhülsen-cylinder clearance of the heat pipe heat engine according to the invention should be a gap width of, for example, 0.1 to 0.15 mm to pass above the piston-Doppelbundhülsen combination resulting working fluid in the liquid form in the direction of warm zone and this at the same time as a sliding film to use. Ideally, the insertion of grooves in the circumference of the piston reduces its friction losses and ensures the sliding film. A slit, for example, in an oblique shape, the double collar facilitates thereby the production of the piston double collar combination.

Preferably, the condensing at the cold zone of the heat pipe heat engine according to the invention working fluid is passed through a connection outside the cylinder to the underside of the piston-double collar combinations in the form that the opening of the connecting line is introduced immediately above the lower end stop in the cylinder. The from the point of view of the cold zone lower opening of the overflow channel (s) should thereby slightly from the axial point of view, for example, 1-2 mm, begin below. This variant of the condensate recirculation prevents an uncontrolled accumulation of condensate above the piston. Furthermore, it is ensured that a pressure equalization via the condensate line to the upper space of the heat pipe heat engine does not take place early, but ideally only when the piston with the movable double collar sleeve has reached the upper position.

Ideally, the flow control of the heat pipe heat engine according to the invention is carried out in such a way that at the beginning of the cyclic process, the piston-double collar combination rests on the lower, the warm zone end stop, as a starting position. At this time, all overflow and other inlets or outlets of the space of the warm zone facing piston underside are closed. Thus, due to the evaporation of the liquid working medium at the warm zone, a corresponding vapor pressure is produced as a function of the selected working medium and the temperature of the hot zone. At the same time, the vapor pressure above the piston decreases due to condensation of the vaporous working medium at the cold zone.

This temporary separation of the spaces of the cold and warm zone represents a decisive difference to the original heatpipe principle used as a pure heat pipe, which is often regarded as quasi-isothermal in the area of the adiabatic zone between the heat source and the heat sink. The heat pipe heat engine according to the invention interrupts the connection of the rooms of the cold as well warm zone cyclically and thereby allows the emergence of a significant difference in temperature of the two steam rooms, resulting in accordance with the vapor pressure curve of the working medium used in a pressure difference between the two rooms. This pressure difference is used according to the invention for generating movement by a piston.

The vapor pressure difference of the heat pipe heat engine according to the invention between the warm zone and the cold zone facing the piston side start the piston movement in the direction of the cold zone. For the selected in this embodiment spring, which is installed slightly biased between the upper piston side and the cylinder wall of the cold zone, a spring constant is selected, which, based on the total stroke of the piston, for example, a spring force of about 10% with respect to the force of Piston at the expected operating conditions. These result approximately from the selection of the working medium, the piston area in the axial direction and the temperatures of the cold and the warm zone. The basis is, inter alia, the vapor pressure curve of the selected working medium.

The piston movement in the direction of the cold zone ideally tensions the spring and thus stores kinetic energy up to the end point of the movement of the piston in the direction of the cold zone. Due to the larger slip stick of the double collar in the cylinder over the Gleitreibungshaftwertes the piston within the double collar sleeve remains the sleeve as long as in its initial position until the piston has carried out its upward movement to the upper of the cold zone facing gutter of Doppelbundhülse.

Subsequently, the double-collar sleeve is also moved by the overpressure still acting on the underside of the piston through the piston in the direction of the cold zone. This movement continues until the hot zone facing overflow channel openings of the cylinder are released by the double collar. An upper end stop of the heat pipe heat engine according to the invention and a phase on the edge of the double collar sleeve facing the cylinder on the cold zone side prevent complete closing of the overflow channels by the double collar sleeve.

According to the invention, a pressure compensation in the direction of cold zone is carried out by the release of the overflow. During this pressure equalization, the pressure difference between the space at the piston top and piston bottom side decreases. The kinetic energy stored in the spring is now used due to the decreasing backpressure of the piston underside by pressure equalization to urge the piston in the double collar in the direction of warm zone. This leads to a further sustained pressure equalization through the overflow through the sustained by the spring force pressure on the warm zone facing the piston side. By the stop of the piston at the warm zone facing gutter of the double collar sleeve this sleeve is also moved towards the warm zone and thus ultimately closes the transfer channels.

Closing the overflow channels of the heat pipe heat engine according to the invention thus separates the connection of the spaces above and below the piston, so that the piston double collar combination their lower end point both by pressure rise on the bottom, pressure drop on the cold zone facing the piston side and the reached bottom limit stop. The movement cycle is thus completed and starts anew.

The basic idea of the generation of movement of a process running cyclically in a closed heat pipe construction on the basis of temperature differences is thus implemented by the heat pipe heat engine according to the invention. Basically, the function is possible with a suitable choice of materials and the working medium in a wide temperature range, which may for example also be well below 0 ° C or far above. The following variants are based on this previously described basic variant of the heat pipe heat engine according to the invention.

A further preferred variant of the invention is to use the kinetic energy of the piston, referred to below as piston 1, to produce a zone of elevated temperature level on the heatpipe heat engine which is above the temperature of the warm zone, for example for heating purposes use. Here, no further supply of energy forms such as electrical or mechanical energy is necessary except for the temperature difference at the heat source and heat sink of the heat pipe heat engine.

It is preferred for this purpose in the cold zone another, smaller in diameter cylinder than that of the basic variant, for example, in the axial direction from the perspective of the piston 1 of the basic variant, in addition to introduce heatpipe heat engine according to the invention.

Furthermore, in this preferred variant of the invention, an additional, adapted in diameter to the smaller cylinder, piston, hereinafter called piston 2, attached with a connection to the original piston 1 in such a way that in the uppermost position of the piston 1 and the small piston 2 in the new additional cylinder is at its uppermost position and the cylinder space above the smaller piston 2 at this time has its minimum volume during the cyclic process.

Ideally, the smaller additionally introduced cylinder protrudes so far into the space of the cold zone that the additional introduced movable piston 2 at the time when the larger piston 1 of the heat pipe heat engine according to the invention is located at the bottom, the warm zone closest end stop , with its entire tread of the piston 2 is just surrounded by the additional smaller cylinder. This ensures both the maintenance of a lubricating film and also prevents blockage of the double piston construction. To guide the spring, it may be helpful to extend this cylinder even further towards warm zone.

The piston 2 of the variant of the heat pipe heat engine according to the invention also has a piston-cylinder clearance of, for example, 0.1 mm to allow small amounts of condensate pass as a sliding film between the cylinder wall and the piston 2 and at the same time a sufficient seal of the existing above the piston 2 space to ensure.

According to the invention, at least one condensate discharge is introduced laterally into the additional smaller cylinder within the closed heatpipe heat engine in order to prevent an accumulation of liquefied working medium above the piston 2. The position of the condensate drain is chosen so that upon reaching the lower position of the piston 2, the opening of the condensate drain is released to the flow of liquefied working medium. Depending on the dimension and operating conditions, these are more than just a condensate drain to attach to the smaller cylinder to ensure the drainage of the condensate. The condensed working medium is passed through a stand-up collar of the cylinder of the piston 1 to the condensate collection point. Thus, an accumulation of condensate is also counteracted above the piston 1.

The space above the smaller piston 2, which is driven by the force of the larger piston 1, is used for compression of parts of the, via at least one via a ball valve automatically controlled suction, supplied vaporous working fluid. The opening of the suction line in the cylinder wall immediately above the lower end stop of the double collar sleeve is also realized, like the overflow channels, by the double collar sleeve. This ensures according to the invention that the intake duct does not open unintentionally but only shortly before the downward movement of the piston 1 and 2 in the direction of the warm zone.

A further improvement of the heat pipe heat engine according to the invention is achieved by inserting a ball valve as close as possible to the space above the piston 2. The at the beginning of the upward movement of piston 2 automatically by the gravity of the ball and the steam flow closing ball valve reduces the compression space above the piston 2 and thus allows the concentration of the trapped by the compression of above the small piston 2 vaporous working medium in a smaller space mainly above Piston 2. Here thus heat energy increased temperature potential can be removed by compression, for example, with liquid heat exchangers.

A further preferred variant of the invention is the operation for generating electricity by means of a coupled to the piston 1 device for operating a power generator, for example in the form of at least one linear generator. In this case, permanent magnets are cyclically moved back and forth near the outer cylinder wall in the heat pipe by the piston drive. Outside the hermetically sealed heatpipe heat engine according to the invention, for example, the windings are mounted with yoke for the induction of electrical energy. The largely pressure-tight piston 2 is omitted in the aforementioned form and is realized accordingly only as a second guide piston with sufficiently large openings for the passage of the vaporous working medium in the cylinder of the transport zone. The spring constant of the spring used must be redetermined and taken into account here.

All previously listed variants of the heat pipe heat engine is limiting in common that the required for the cycle cold and warm zone is mounted directly above or below the piston-double collar-sleeve combination in the axial direction, which can be structurally complex. Furthermore, the condensation area required for the cold zone causes a relatively large, volume of the cold zone facing the piston 1, which has a negative effect on the efficiency of the heat pipe heat engine. Also, more flexible positions of cold and warm zone would be beneficial for practical use. The required for the return transport of the liquid working fluid to the warm zone height difference in the axial direction between the liquid boundary of the used in the lower part of the cold zone standing collar collecting liquid working fluid and before the lower end stop of the double collar, from the axial view, entering the room liquid Inlet conditioned, taking into account the spring constant the spring used and the density of the working medium, a minimum height between the lower end stops of the double collar and the stand-up collar, added to the height of the cold zone. This causes a high weight of the double piston construction and results in a large volume on the cold zone side of the piston 1.

A further embodiment of the heat pipe heat engine according to the invention therefore represents the use of external heat exchangers for both the cold and for the warm zone. A dimensioning of evaporation and condensation area and thus of performance parameters of the heat pipe heat engine is so simple and inexpensive possible. While the evaporator or the evaporator of the warm zone, from a vertical point of view, are to be positioned approximately at the level of the liquid boundary of the warm zone and the vaporous working medium is supplied below the piston 1 in the region of the warm zone, or the condenser / s of the cold Zone horizontally and vertically be freely positioned, as long as the liquid column in the return line from the condenser to the liquid inlet, above the lower end stop of the double collar, their minimum height, taking into account the spring constant of the spring used and the density of the working medium, for example, 40 cm vertical view without condensation build up in the condenser. The capacitor is ideally inclined in the direction of the liquid line.

For further embodiment of the invention, at least one connection from the volume, from the axial point of view, above the piston 1 to the condenser for the supply of the gaseous working medium to the condenser attached. The condensation process in the external condenser thus reduces the vapor pressure corresponding to the vapor pressure curve of the working medium in the region of the condenser, which also has the effect of reducing the vapor pressure via the connection to the space above the piston 1 there.

The, from the axial point of view, above the piston directly in the housing of the invention missing capacitor, which is displaced externally in this variant, makes it possible to reduce the volume above the piston 1, in its uppermost position from the axial point of view, to a minimum and to shorten the connecting element to a piston 2, for example, and reduce in weight, which increases the overall efficiency of the heat pipe heat engine according to the invention.

In this variant of the invention, the temperature difference between the evaporator (s) of the warm zone and the condenser (s) of the cold zone thus produces a vapor pressure difference between the two working chambers of the piston 1, which is triggered by the upward movement of the piston 1 then triggered from the axial point of view then also pushes upwards over the stop of the piston 1 at the upper edge of the double collar sleeve and thus releases the overflow channel (s). During the entire upward movement of the piston-double collar combination mechanical work on the tension of the spring and mechanical energy is provided on, connected to the piston 1, connecting element, which is used according to the invention.

Furthermore, in this variant of the heatpipe heat engine, the condensate line, from the axial point of view slightly above, for example, 1 to 2 mm higher than the lower outlet of the / the overflow / on the cylinder attached, so that the pressure compensation to space above the piston 1 and thus an increase in pressure in the condenser can take place and subsequent opening of the condensate line, in upward movement of the double collar, condensate can enter below the piston 1.

According to the invention, the absolute upper end stop for the upward movement of the double collar, in this variant of the heatpipe heat engine, realized by the reduced diameter cylinder housing, from the axial view above the piston 1. The beginning pressure equalization with release of the / the overflow channel / -alle as well as the back pressure of the spring should ideally be adjusted in the form that a stop of the double collar at the upper end stop as possible avoided.

The pressure equalization of the existing pressure difference between the spaces above and below the piston 1, which now begins via the overflow channel (s), is carried out according to the invention until the spring force of the spring is sufficient to urge the piston 1 inside the double collar sleeve in the direction of the warm piston side. until it reaches, from the axial point of view, the lower edge of the double collar sleeve and also pushes it down until the overflow channel (s) are closed.

Ideally, the end stops facing the underside of the piston 1 are arranged at such a distance from the outlet of the overflow channel (s) that, if the temperature difference between the warm and cold zone of the heat pipe heat engine persists, the double collar does not reach the bottom end stops, but already before reaching these end stops by the rebuilding pressure difference between the piston top and piston bottom side of the piston 1, the piston 1 is urged in the direction of cold zone within the double collar.

In accordance with the invention, in direct operation of the heatpipe heat engine, direct stops of the double collar-piston combination on the housing parts thus fail to take place, which, in combination with the omission of moving valve parts, enables low-noise operation.

In this variant of the invention, a process which proceeds automatically by a temperature difference between the hot and cold zone of the heat pipe heat engine according to the invention is thus realized and the cycle is completed, so that it starts over again when the temperature difference between the cold and the warm zone exists.

A variant according to the invention of the use of the mechanical energy provided by the invention on pistons 1 consists in the circuit realized in a second circuit via the piston 2 for the compression of gaseous working medium. About 2 valves, such as ball valves, attached to the inlet and outlet of the working space above the piston 2, at least one evaporator, at least one throttle body, at least one capacitor and the connection of said components, as in refrigeration circuits, for example, known from refrigerating machines or heat pumps, the supplied by piston 1 mechanical energy for performing compression work with piston 2 in said cycle, hereinafter referred to as circuit 2 used.

Thus, according to the invention, the possibility of the heat pipe heat engine for cooling purposes with the help of the evaporator of the circuit 2 made available cooling capacity to use or alternatively to use the provided on the condenser of circuit 2 heat energy, for heating purposes, for example.

Furthermore, depending on the specified application, cooling or heating, due to the compression ratio of the piston 1 and 2 at the evaporator of the circuit 2, a lower temperature than that at the cold zone and the condenser of the circuit 2, a higher temperature than that at the evaporator Heatpipe heat engine to be tapped. Thus, the efficiency can be increased when used for cooling purposes, the heat output to the condenser of the circuit 2 via heat exchangers are fed to the evaporator heatpipe heat engine. When heating purpose, the efficiency of the cooling capacity of the evaporator of circuit 2 can be supplied to the condenser of the heatpipe heat engine efficiency.

The displacement of the condenser and evaporator of the heat pipe heat engine according to the invention externally allows, increasing the thermal efficiency, further the thermal insulation of all other components except the evaporator and condenser elements.

A further preferred variant of the invention is the embodiment as a heat pipe heat engine with capillary force-driven condensate transport. In this case, a capillary structure, which is realized, for example, on the inside of the cylinder of piston 1, as known under the designations "mesh", "groove" or "sinter", is responsible for the transport of condensate, within limits also against gravity , The capillary force driven variant of the heat pipe heat engine according to the invention, as the basic variant of the heat pipe heat engine according to the invention or its sub-variants operated. The only difference here is the transport of condensate through the exemplary intake of a smooth inner cylinder tube to ensure a pressure-tight and low-wear operation of the piston-Doppelbundhülsen combination in the cylinder area. The construction of the inner tube must ensure the transport of liquids and steam, especially in the area of the heat sink and the heat source, as is known with capillary-driven heatpipes.

Furthermore, due to the system, in the reverse position of the cold and warm zone of a heat pipe heat engine according to the invention with capillary force driven condensate transport, the construction of piston double collar and spring must be introduced in the reverse direction in the heat pipe heat engine according to the invention. The spring and / or further measures for resetting the piston-double collar combination are thus usually on the side of the cold zone of the heat pipe heat engine. The bias voltage in the initial position of the piston 1 and the spring constant of the spring used is adapted depending on the purpose of the invention in the form that the provision of the piston-double collar combination is ensured in their initial position under the respective operating conditions of the intended use.

As a further variant, mechanisms such as tension springs on the side of the warm zone are possible. However, the constructive effort increases here, wherein by a displacement of the return mechanism, in the form of, for example, at least one tension spring on the side of the warm zone, the so-called dead space volume of the gas space on the side facing the heat sink piston side is ideally reduced.

In a further preferred variant of a heat pipe heat engine with capillary-force-driven condensate transport, the heat sink is designed as an external capacitor, which is also in this variant of the heat pipe heat engine according to the invention in reducing the dead space volume of the gas space on the side facing the heat sink piston side and thereby efficiency-increasing effect. In this variant of the invention, too, the external condenser is to be tilted in the direction of the condensate inlet opening in order to ensure the condensate drainage.

Another embodiment of the heat pipe heat engine according to the invention with capillary force driven condensate transport is the use of an external capacitor as a heat sink, which also in the region of the condensation surface of the capacitor and the connection to the capillary between the inner and outer wall of the capillary force driven heat pipe heat engine, a capillary structure, such as for example, under the designations "mesh", "groove" or "sinter" known. This variant of the heatpipe heat engine with capillary-powered condensate transport allows, with appropriate dimensioning of the capillary structure, a position and gravity-independent operation.

A further embodiment of the heatpipe heat engine according to the invention with capillary force-driven condensate transport is the variant with external evaporator as a heat source. The condenser equipped with capillary structure on the condenser in this variant of the invention completely filled with capillary compound with the also equipped with capillary Connected evaporator. The evaporator is in turn connected to the gas space of the heat source side facing the piston 1. A direct compensation of vapor pressure between the cold zone in the form of the condenser and the warm zone in the form of the evaporator is prevented in this variant of the invention by the capillary structure in the connection between condenser and evaporator, which is known, for example, under "mesh" or "sinter".

The displacement of the warm zone, in the form of a likewise connected to the capillary evaporator, externally makes the collection of an inner cylinder and between the inner and outer cylinders otherwise necessary for the condensate transport capillary unnecessary. The evaporation and condensation performance can be dimensioned so flexible and the structure of the overall construction, despite position and gravity-independent use, greatly simplified. The dimensioning of the volume of the capillary structure in the evaporator, condenser and their connection should be taken into account in order to ensure a sufficient amount of condensate for continuous evaporation over the entire temperature range of use of the invention. The possibility of supplying, for example by compression work additionally incurred heat energy in or on the warm zone facing gas space remains.

A further improvement in the efficiency of the heat pipe heat engine according to the invention is in variants with capillary-powered condensate transport by laying the opening of the connection to the external condenser from the gas space of the cold zone to a position laterally on the master cylinder, near the axial view of the cold zone facing End stops, reached. The condensation power in the external capacitor during the overflow phase remains by this measure for the subsequent working phase in the form of negative pressure relative to the gas space of the stored cold zone in the master cylinder in the region of the externally displaced capacitor until the double collar sleeve releases the opening to the condenser to the end of the overflow phase.

Also in the variants of the invention with capillary-powered condensate transport, it is possible to use the generated mechanical energy, for example via linear generators, to generate electrical energy based on thermal energy.

Regardless of the variants of the heat pipe heat engine according to the invention also apply to this invention, the laws of the Carnot cycle and the context defined in this connection possible efficiency of heat engines and the definitions of exergy and anergy shares, taking into account temperature differences and absolute temperature. Generally, then, as usual with heat engines, the potential efficiency increases as the temperature difference between the warm and cold zones increases. With a suitable choice of the working medium, an increase in efficiency can still be achieved with the same temperature difference but lower absolute operating temperature. Regardless of the efficiency, the power output is due to the heatpipes transferable power density in one for the commercially useful range.

The basic idea of a low-cost, low-moving parts, based on existing principles and to be realized with ordinary components heatpipe heat engine for commercial use can be implemented in all embodiments of the proposed invention. The heat pipe heat engine according to the invention may preferably be designed and manufactured as a gravity-driven two-phase thermosiphon or as a capillary force-driven heatpipe heat engine. The combination of features kostengünster structure, usable power density and characterized by only thermal energy drive characterize the heat pipe heat engine according to the invention.

The heat pipe heat engine according to the invention, which can be considered in principle as a heat engine, is ideally suited for heat and power in small and medium sized systems, decentralized power supplies both thermal and electrical type in a wide temperature range. For example, heating systems in conjunction with geothermal energy, any use of waste heat for electricity production, the use of solar energy, for example, with temporary storage of thermal energy or the use for cooling purposes even position and gravity-independent called. The possible fields of application are extremely diverse. The profitability is ensured by principally maintenance-free operation and use of existing temperature difference potentials.

• Fig. 1 eine Heatpipe-Wärmekraftmaschine der vorliegenden Erfindung.
• Fig. 2 eine Anordnung einer Heatpipe-Wärmekraftmaschine der vorliegenden Erfindung.
• Fig. 3 eine Anordnung einer Heatpipe-Wärmekraftmaschine der vorliegenden Erfindung.
• Fig. 4 eine Anordnung einer Heatpipe-Wärmekraftmaschine der vorliegenden Erfindung.

With reference to subsequent drawings, the invention will be explained in more detail in the illustrated embodiments. Further features of the invention will become apparent from the following description of the embodiments, the invention and the accompanying drawings with the claims.

• Fig. 1 a heatpipe heat engine of the present invention.
• Fig. 2 an arrangement of a heat pipe heat engine of the present invention.
• Fig. 3 an arrangement of a heat pipe heat engine of the present invention.
• Fig. 4 an arrangement of a heat pipe heat engine of the present invention.

The Fig. 1 shows the arrangement of a hermetically sealed designed as a piston engine Heatpipe heat engine according to the invention 1, with a cylinder 21 and a movably mounted in the cylinder 21 double collar sleeve 22 in which the movably guided piston 13 is mounted. The piston 13 is connected via a fixed connection 28 with the smaller diameter than piston 13 pronounced piston 5 . The combination of the double collar 22 and the piston 13 and 5 with compound 28 are pressed by spring 29 under defined spring pressure in the region of the end stops 15 and 24 in the direction of heat source 18 .

In the Fig. 1 illustrated Heatpipe heat engine 1 according to the invention has a further cylinder 30, which is smaller in diameter than the main cylinder 21 and the cylinder head 3 , in which the piston 5 in the working space 4, the entering through the intake 2 vaporous working medium 16 compresses. In the transport zone between the end stops 24 and 15 of the heat pipe heat engine 1 according to the invention, the overflow channels 23 are introduced with the openings 12, 14 and 20 for the overflow of the vaporous working medium 16 . Near the bottom of the heat source nearest openings 14 and 20 are the intake duct 26 for vaporous working medium 27 for filling the cylinder chamber 4 and the condensate line 11 for recycling the liquefied by condensation working medium 16 from the condensate collecting channel 10, attached.

In Fig. 1 is shown that both on the cylinder head 3 as well as on the heat sink 9 during the condensation process heat energy is released and condensate 7 is formed. The condensate from cylinder chamber 4 is fed via line 6 of the collecting channel 10 . The so-called transport zone of the heat pipe heat engine 1 according to the invention and the suction line 26 with ball valve 31 is thermally insulated with insulating material 25 . The heat pipe heat engine 1 according to the invention sets a volume change of an in-cylinder 19 between the piston 13 and the heat source 18 working medium 16 via the axially displaceable piston 13 and the axially displaceable double collar 22 in an upward movement of the connected pistons 13 and 5 and the double collar 22 ,

Fig. 1 shows that the upward movement of pistons 13 and 5 first occurs until the piston 13 abuts the upper stop within the double collar 22 and then pushes them also in the direction of heat sink 9 . Spring 29 of the heat pipe heat engine 1 according to the invention is tensioned during the movement of the piston 13 in the direction of cold zone 9 . The upward movement of the piston 13 and the double collar sleeve 22 is terminated as soon as the double collar sleeve 22 releases the lower openings 14 and 20 of the overflow channels 23 by its upward movement in the direction of the cold zone 9 . Balancing the between the space 8 of the cold zone and the space 19 of the warm zone at this time existing pressure difference begins by the opening of the overflow channels 23. The decreasing by this compensation pressure difference reduces the pressure on the hot zone 18 facing side of the piston 13 to the pressure on the piston top by the spring 29 outweighs and this within the double collar 22nd in the direction of warm zone 18 urges.

Is the piston 13 of the heat pipe heat engine 1 according to the invention in Fig. 1 arrived at the lower collar of the double collar sleeve 22 , this is also by the spring force of the spring 29 and the momentum of the mass of the piston 13 and 5 and their connection 28 in the direction of warm zone 18 to the closure of the lower openings 14 and 20, but a maximum of End stop 15 pressed. The supply of external heat energy to the heat source 18 generates at existing temperature difference between the heat sink 9 and heat source 18 continuously steam in the room 19 while condensed in space 8 constantly vaporous working medium 16 and thus the vapor pressure is reduced, resulting in a pressure difference between the rooms 19 and 8 , This sustained thermodynamic cycle within the heat pipe heat engine 1 according to the invention restarts the process, so that a cyclical and independently starting movement process is realized.

The Fig. 2 shows the arrangement of a hermetically sealed, constructed as a piston engine Heatpipe heat engine according to the invention 1, with a cylinder 21 and a movable in the cylinder 21 double collar sleeve 22 in which the movably guided piston 13 is mounted. The piston 13 is connected via a fixed connection 28 with the smaller diameter than piston 13 pronounced piston 5 . The combination of the double collar 22 and the piston 13 and 5 with compound 28 are pressed by spring 29 under defined spring pressure in the region of the end stops 15 and 53 in the direction of the gas space 19 of the warm zone.

In the Fig. 2 illustrated Heatpipe heat engine 1 according to the invention has a further cylinder 30 which is smaller in diameter than the main cylinder 21 and the cylinder head 3 , in which the piston 5 in the working space 4, the incoming through suction 2 vapor working medium 37 compresses. In the area of the transport zone, near the end stops 53 and 15, the heatpipe heat engine 1 according to the invention, the overflow channel (s) 23 are introduced into the space 8 with the openings 20 and 32 for overflowing the vaporous working medium from space 19 .

Fig. 2 shows, from the axial view above the highest position of the piston 13 in the region of the space 8, the opening 46 of the connection 45 for supplying the gaseous working fluid 41 to the external capacitor 42 as a cold zone of the invention. The inclined in towards the connection 11 condenser 42 condensing the working medium passes into the compound 11, and thus collects in this as a liquid column of the condensed working medium 7 with the liquid level 43. flows Upon release of the opening 14 by the double collar sleeve 22 by the previously executed surge at opening 46 and the pressure of the liquid column in connection 11, the liquid working medium 7 in the space below the piston 13 a.

In Fig. 2 also shown in the, from the axial view bottom portion 18 of the heat pipe heat engine according to the invention 1 collected liquid working medium 16, which is vaporized via the connection 51 to the external evaporator 50 for evaporation with the aid of supplied heat energy to vaporous working medium 49 and via the connection 48 and opening 47 to the space 19, below the piston 13, is supplied. The cycle of the working medium 16 is closed.

Fig. 2 further shows that the so-called dead volume of volume 8 above piston 13 is reduced by the displacement of the cold zone to the outside, in the form of condenser 42, and the connection 28 is also reduced in length and thus weight, which reduces the efficiency of the Heatpipe heat engine according to the invention increases. Furthermore, by displacing the condenser 42 and the evaporator 50 externally, the invention can be used flexibly.

In Fig. 2 is also shown that by the piston 5, driven by piston 13 via the connection 28, the cylinder chamber 4, the valves 31 and 38, which are for example designed as check valves in the form of ball valves, the compounds 40 and 26, a throttle member 34, the openings 2 and 36 and the condenser 35 and evaporator 33, depending on the structural design, a compression refrigeration machine or alternatively, a heat pump can be realized, which is driven by heat energy as an energy source. The unused energy of the condenser 35 or evaporator 36 is thereby, depending on the intended use, as known in refrigerant circuits, via heat exchanger to the evaporator 50 or condenser 42 to increase efficiency.

Fig. 2 shows that the upward movement of pistons 13 and 5 first occurs until the piston 13 abuts the upper stop within the double collar 22 and then pushes them also in the direction of upper end stop 53 . Spring 29 of the heat pipe heat engine 1 according to the invention is tensioned during the movement of the piston 13 in the direction of the upper end stop 53 . The upward movement of the piston 13 and the double flange sleeve 22 is stopped as soon as the double collar sleeve 22, the lower openings 20 and 14 of the / of the overflow channel / -äle 23 and the condensate inlet 11 releases its upward movement towards the top end stop 53rd The equalization of the existing between the space 8 and the space 19 at this time pressure difference begins by the opening of the / the overflow channel / -alle 23. The compensation of existing at this time pressure difference between the piston top and piston bottom of the piston 13 is continued until the pressure on the space 8 facing the piston top side of the piston 13 outweighs by the spring 29 and urges them within the double collar 22 in the direction of space 19 .

Is the piston 13 of the heat pipe heat engine 1 according to the invention in Fig. 2 arrived at the lower collar of the double collar sleeve 22 , this is also by the spring force of the spring 29 and the momentum of the mass of the piston 13 and 5 and their connection 28 in the direction of space 19 to the closure of the lower openings 14 and 20, but maximum to the end stop 15, pressed. The supply of external heat energy to evaporator 50 generates at existing temperature difference between the heat sink 42 and heat source 50 continuously steam in space 19, while condensed in condenser 42 constantly vaporous working fluid 41 and thus the vapor pressure via compound 45 is reduced in space 8 , resulting in a pressure difference between the rooms 19 and 8 leads. This thermodynamic cycle within this variant of the invention Heatpipe heat engine 1 starts the movement process again, so that a cyclic and independently starting motion process is realized.

The Fig. 3 shows the arrangement of a hermetically sealed, designed as a piston engine with capillary force-driven condensate transport, heat pipe heat engine according to the invention 1, with an outer cylinder 21, an inner cylinder 54 and a movably mounted in the inner cylinder 54 double collar sleeve 22, in which movably guided piston 13 is mounted. The piston 13 is connected via a fixed connection 28 with the smaller diameter than piston 13 pronounced piston 5 . The combination of the double collar 22 and the piston 13 and 5 with compound 28 are pressed by spring 29 under defined spring pressure in the region of the end stops 15 and 53 in the direction of the gas space 19 of the warm zone. Spring constant and bias of spring 29 are to be redetermined in this variant of the invention, wherein the bias of spring 29 has a value which allows it to piston 13 and connected thereto piston 5 against the compression resistance of the compressed working fluid 37 in the starting position of Push piston 13 until double collar 22 closes the opening 20 .

In the Fig. 3 illustrated Heatpipe heat engine 1 according to the invention has a further cylinder 30 which is smaller in diameter than the inner cylinder 54 and the cylinder head 3 , in which the piston 5 in the working space 4, the incoming through suction 2 vaporous working medium 37 compresses. In the operating mode chiller cylinder head 3 is introduced in the gas space 19 . The positions 36, 38, 52, 40, 35, 33, 26, 37, 31 and 2 represent by way of example the components known from refrigerant circuits. In the region of the transport zone, near the end stops 53 and 15 of the heat pipe heat engine 1 according to the invention , the overflow channel (s) 23 with the openings 20 and 32 are introduced into the space 8 for overflowing the vaporous working medium from the space 19 .

Fig. 3 shows, from the axial view below the lowest position of the piston 13 in the region of the space 8, the opening 46 of the connection 45 for supplying the gaseous working fluid to the external capacitor 42 as a cold zone of the invention. The condensation surface of the condenser 42, the connection 11, the gas chamber 19 facing side of the cylinder head 3 and the space between the outer cylinder 21 and inner cylinder 54 have a capillary 55, 55 ', 55 ", as of heat pipes, for example, under the names The working medium condensing on the capillary structure 55 ' in the condenser 42 is transported by the capillary forces along the capillary structure in connection 11, through opening 14 to the capillary structures 55 and 55 " . Regardless of the equipment of the capacitor 42 and compound 11 with a capillary structure, the capillary-driven condensate transport takes place in the capillary structures 55 and 55 " regardless of the position of the double collar 22 , as long as liquid working medium is applied to opening 14 and by supplying heat energy to the warm Zone 18 liquid working medium evaporates through the openings 57. If capacitor 42 and connection 11 also have a capillary structure, this variant of the heat pipe heat engine 1 according to the invention can be used independently of position and gravity.

In Fig. 3 Furthermore, it is shown that in the, from the axial view, upper region 18 of the heat pipe heat engine 1 according to the invention via the capillary structure 55, 55 ', 55 "the warm zone 18, and the air heated by compression work cylinder head evaporates 3 supplied liquid working medium and so arises in existing temperature difference between heat sink 42 and heat source 18, continuously vapor pressure according to the vapor pressure curve of the working medium. In this variant of the present invention heat pipe heat engine 1 The vapor pressure in gas space 8, according to the vapor pressure curve, is reduced in, from the axial view, the upper initial position of piston 13 and double collar 22 by condensation of the vaporous working medium in condenser 42. This results in the downward movement of piston 13 into double collar 22, from the axial point of view This reaches the lower end stop of the double collar sleeve 22 and urges it towards the end stop 53. In this case, the spring 29, which already has a pretension in the upper starting position, is tensioned while supplying mechanical energy.

In Fig. 3 is also shown that the downward movement of the double collar 22 is performed until the opening 20 of the / the overflow channel / channels 23 is released by double collar 22 and a pressure equalization of the existing at that time pressure difference between the gas chambers 19 and 8 begins. The compensation of the present at this time pressure difference between the piston top and piston bottom of the piston 13 is continued until the pressure on the piston bottom of the piston 13 outweighs by the spring 29 and urges it within the double collar 22 in the direction of space 19 . If the piston 13 of the heat pipe heat engine 1 according to the invention reaches the upper collar of the double collar 22 , this is also by the spring force of the spring 29 and the momentum of the mass of the piston 13 and 5 and their connection 28 in the direction of space 19 to the closure of the opening / s 20, but maximum pressed to the end stop 15 . Also in this variant of the heat pipe heat engine 1 according to the invention, a cyclical and independently starting movement process is thus realized via the continuing thermodynamic cycle.

Fig. 3 further shows that the so-called dead volume of volume 8, from the axial point below piston 13, by the displacement of the cold zone to the outside, in the form of capacitor 42, also in this variant of the heat pipe heat engine 1 according to the invention is reduced. The embodiment according to the invention with capillary-force-driven condensate transport furthermore allows a shortened connection 45 to increase efficiency . Ideally, the volume of the gas space 8 is as small as possible by constructive measures such as 56 at the lowest point of the piston 13 from the axial point of view, the cold zone , It must be ensured that the piston 13 is not prevented from adhering to housing parts on the return process exerted by the spring force of the spring 29 into its initial position.

The Fig. 4 shows the arrangement of a hermetically sealed, designed as a position and gravity independent piston engine heatpipe heat engine according to the invention 1, with a cylinder 21, and a movably mounted in the cylinder 21 double collar sleeve 22 in which the movably guided piston 13 is mounted. The piston 13 is connected via a fixed connection 28 with the smaller diameter than piston 13 pronounced piston 5 . The combination of the double collar 22 and the piston 13 and 5 with compound 28 are pressed by spring 29 under defined spring pressure in the region of the end stops 15 and 53 in the direction of the gas space 19 .

In the Fig. 4 illustrated Heatpipe heat engine 1 according to the invention has a further cylinder 30 which is smaller in diameter than the main cylinder 21 and the cylinder head 3 , in which the piston 5 in the working space 4, the incoming through suction 2 vapor working medium 37 compresses. In the operating mode chiller cylinder head 3 is introduced in the gas space 19 . The positions 36, 38, 52, 40, 35, 33, 26, 37, 31 and 2 represent by way of example the components known from refrigerant circuits. In the region of the transport zone, near the end stops 53 and 15 of the heat pipe heat engine 1 according to the invention , the overflow channel (s) 23 with the openings 20 and 32 are introduced into the space 8 for overflowing the vaporous working medium from the space 19 .

Fig. 4 shows, from the axial point of view laterally the lowest position of the piston 13 in the region of the space 8, the opening 46 of the connection 45 for supplying the gaseous working fluid to the external capacitor 42, as a cold zone of the invention, which on the condensation surface a capillary 55 ' comprising, the connection 58, which has the capillary structure 55 ' over the entire cross section and the entire volume, the externally displaced evaporator 50, as a warm zone of the invention, which on the evaporation surface the capillary structure 55' , and compound 48, which in Opening 47 opens to gas space 19 . The working medium condensing on the capillary structure 55 ' in the condenser 42 is transported by the capillary forces along the capillary structure 55' in connection 58 to the capillary structure 55 ' in evaporator 50 , where it evaporates with the supply of heat energy and enters the gas space 19 in vapor form via connection 48 .

In Fig. 4 is also shown, the displacement of the opening 46 of the heat pipe heat engine 1 according to the invention to a, from the axial view, located above the end stop 53 position in cylinder 21, which by using a compound 58, the capillary structure over the entire cross section 55 ' has , is possible and increases efficiency in terms of the volume of vapor to be condensed of the working fluid per duty cycle and the return process of piston 13 into its initial position during the overflow phase. The end stops 53 are executed in this variant to further increase efficiency without construction, as by the material thickness of the double collar 22 is a sufficiently large distance between, from the axial view, lower housing wall and piston 13 at the bottom, the end stops 53 nearest, position of piston 13 and the dead space volume of gas space 8 is thus minimized.

Named patent literature

• DE 10 2005 040 866 B3
• WO 2014/012586 A1

Claims (15)

Heatpipe heat engine ( 1 ) having at least one cylinder ( 21 ), with a in the cylinder ( 21 ) movably guided double collar sleeve ( 22 ), in the double collar sleeve ( 22 ) movably guided piston ( 13 ), with at least one connection ( 28 ) and at least one further piston ( 5 ), with at least one spring ( 29 ), with at least one cold zone ( 9 ), with at least one warm zone ( 18 ) and end stops ( 15, 24 ) for the double collar sleeve ( 22 ). Furthermore, the heatpipe heat engine ( 1 ) at least one working medium ( 16 ) in liquid form, at least one space ( 19 ) with connection to the warm zone ( 18 ) facing side of the piston ( 13 ) for expansion of the evaporating working fluid ( 16 ) , Furthermore, the heat pipe heat engine ( 1 ) has at least one overflow channel ( 23 ) with the openings ( 12 , 14 ) between the end stops ( 15 , 24 ). The spring ( 29 ) has already at the lowest, the warm zone ( 18 ) closest to the position of the piston ( 13 ) has a low bias. Heatpipe heat engine according to claim 1, characterized in that the heatpipe heat engine ( 1 ) as a gravity-driven variant on, from a vertical point of view, the lower end of the heat sink ( 9 ) a condensate collection trough ( 10 ) and at least one connection ( 11 ) of the Condensate collecting channel ( 10 ) for at the lower end stop ( 15 ) in the cylinder ( 21 ) entering the opening ( 14 ). Heatpipe heat engine according to claim 1 or 2, characterized in that at the cylinder wall opening ( 20 ) opens a connection ( 26 ) in a valve ( 31 ), which closes automatically at overpressure in space ( 4 ) and at negative pressure in space ( 4 ) automatically opens to let vaporous working fluid ( 27 ) into the working space ( 4 ) of the cylinder ( 30 ) via inlet port ( 2 ) to flow during downward movement of the piston ( 5 ). Line ( 26 ), valve ( 31 ) and the entire transport zone of heat pipe heat engine ( 1 ) are thermally insulated by an insulating material ( 25 ). Furthermore, the cylinder ( 30 ) has at least one condensate discharge device ( 6 ) for discharging condensate formed in space ( 4 ) in the direction of the condensate channel ( 10 ). Heatpipe heat engine according to one of the preceding claims, characterized in that it displaces in a variant, a cold zone in the form of at least one capacitor ( 42 ) and the warm zone in the form of at least one evaporator ( 50 ) to the outside and thus externally of the housing construction and thus the space ( 8 ) has a small dead space volume. Furthermore, the heat pipe heat engine ( 1 ) has at least one connection ( 45 ) from space ( 8 ) to condenser ( 42 ) and at least one connection ( 11 ) from condenser ( 42 ) to opening ( 14 ). Heat pipe heat engine according to claim 4, characterized in that it comprises the end stops ( 15, 53 ) for the double collar ( 22 ) and at least one overflow channel ( 23 ) with the openings ( 20 , 32 ), wherein opening ( 32 ) in space ( 8 ) opens. Heatpipe heat engine according to one of the preceding claims, characterized in that it compresses in a variant in the space ( 4 ) via opening ( 2 ) sucked gaseous working medium ( 37 ) and in an optional as chiller or heat pump auslegbaren, preferably external, with the components valve ( 38 ), compound ( 40 ), condenser ( 35 ), throttle body ( 34 ), evaporator ( 33 ), connection ( 26 ) and valve ( 31 ) uses. Increases efficiency in the case of the design as a chiller the condenser ( 35 ) resulting heat of condensation via heat exchanger to the evaporator ( 50 , 18 ) or when designed as a heat pump to the evaporator ( 33 ) resulting refrigeration capacity via heat exchanger to the condenser ( 42, 9 ). Heatpipe heat engine according to one of the preceding claims, characterized in that the piston ( 5 ) in the region of the gas space ( 19 ) of the warm zone via connection ( 28 ) with piston ( 13 ) is connected and the spring ( 29 ) below, in the End stop ( 15 ) nearest starting position of piston ( 13 ), defined preload, in the region of the gas space ( 8 ) of the cold zone, pressure in the direction of warm zone on piston ( 13 ) exerts. Heatpipe heat engine according to claim 7, characterized in that in a variant with capillary force driven condensate transport between the cylinder ( 21 ) and in the region of the warm zone ( 18 ), vapor-permeable inner cylinder ( 54 ) and on the cylinder head ( 3 ) has a capillary structure comprises (55, 55 "). Further, it has a cold zone in the form of at least one capacitor (42) to the outside, and thus external to the housing construction shifted to that for the purpose of condensate drain in the direction of connection (11) is inclined, in turn, with a gradient inclined to the opening ( 14 ). Heatpipe heat engine according to one of the preceding claims, characterized in that it has a capillary structure ( 55 ' ) in a position-independent and gravity-independent variant in total volume and cross-section of compound ( 11 ) and on the condensation surface of the condenser ( 42 ) over the entire condensation region of the condenser ( 42 ) of vaporous working medium from compound ( 45 ) is achieved. Heatpipe heat engine according to one of the preceding claims, characterized in that in a further position and gravity-independent variant in addition to the externally, in the form of condenser ( 42 ), displaced cold zone and a displaced to the outside warm zone in the form of Evaporator ( 50 ) and a connection ( 58 ) between the condenser ( 42 ) and evaporator ( 50 ). Room ( 8 ) is connected via connection ( 45 ) with condenser ( 42 ) and space ( 19 ) via connection ( 48 ) with evaporator ( 50 ). The evaporator area of evaporator ( 50 ), the condensing area of condenser ( 42 ) as well as the entire volume and cross section of junction ( 58 ) have a capillary structure ( 55 ' ) as known under the designations "mesh" or "sinter" , wherein the capillary structure ( 55 ') in connection ( 58 ) prevents a direct vapor pressure equalization between evaporator ( 50 ) and condenser ( 42 ). Inner cylinder ( 54 ), opening ( 14 ) and capillary structure ( 55 , 55 " ) omitted according to the invention in this variant. Heatpipe heat engine according to one of the preceding claims, characterized in that in a variant with the use of capillary structure ( 55 ' ) in connection ( 11 , 58 ) and at least one external capacitor ( 42 ) one in the outer cylinder ( 21 ) near the end stop ( 53 ) displaced opening ( 46 ), which at the end stop ( 53 ) closest position of Doppelbundhülse ( 22 ) of this, during the phase of the pressure equalization between the spaces ( 19 ) and ( 8 ) is closed. Heatpipe heat engine according to one of the preceding claims, characterized in that the overflow channels ( 23 ), the openings ( 12 , 14 , 20 ), the double collar sleeve ( 22 ), piston ( 13 ), the spring ( 29 ) and the end stops ( 15 , 24 , 53 ) perform the flow control of the heat pipe heat engine ( 1 ) automatically. Heatpipe heat engine according to one of the preceding claims, characterized in that the working medium ( 16 ) used in the inside and outside of the heatpipe heat engine ( 1 ) existing operating conditions at the warm zone ( 18 , 50 ) can evaporate and at the cold zone ( 9 , 42 ) a condensation can take place. Heatpipe heat engine according to one of the preceding claims, characterized in that the compressor piston ( 5 ) is designed as a pure guide piston without compression function and via a connection to piston ( 13 ) a permanent magnet construction near the outer wall ( 21 ) cyclically back and forth is moved so that outside the hermetically sealed heatpipe heat engine ( 1 ) by induction electrical energy can be removed, such as in the form of linear generators. Heatpipe heat engine according to one of the preceding claims, characterized in that as the lubricant, the working medium ( 16 ) is used and the materials of the piston ( 13 , 5 ), cylinder ( 21 , 30 , 54 ) and double collar sleeve ( 22 ) in their compatibility thereon be matched.

Images