DE102008010059A1 - Mechanical energy producing device for stirling engine, has valve devices locking working fluid volumes against flow direction, where pressure gradient, which is caused downstream to flow path, is reduced by opening devices in direction - Google Patents

Abstract

The device has a fluid container (B1) provided downstream to another fluid container (B2). Valve devices (V12, V23, V34) lock working fluid volumes against a flow direction and are opened in the flow direction. A pressure increasing unit causes an increase of the pressure of a working fluid (AF) e.g. air, in the container (B1) by effect of a heat source in a partial cycle in cyclically alternating manner. A pressure gradient, which is caused downstream to a flow path, is reduced by opening the valve devices in the flow direction. An independent claim is also included for a method for producing mechanical energy from a temperature difference between a heat sink and a heat source.

Description

The The invention relates to an apparatus and a method for obtaining of mechanical energy from the temperature difference between a heat source and a heat sink.

to Obtaining mechanical energy using a temperature difference between a heat source and a heat sink In particular, the Stirling engine is known, which in feed from heat to one end of one at the other end cooler Cylinder a linear oscillating movement of a piston in the Cylinder starts.

In the US 6240729 B1 a device for converting thermal energy into mechanical energy is known in which a fluid circuit contains at least three chambers and check valves connected by fluid lines. The chambers are mounted on a rotatable frame so that a chamber is immersed in a liquid serving as a heat source. In the submerged chamber, a working fluid circulating in the fluid circuit is partially vaporized, thereby displacing working fluid in the circuit and displacing the center of gravity so as to place the frame in an unidirectional rotation.

Of the present invention is based on the object, an advantageous Device and method for obtaining mechanical energy from the temperature difference between a heat source and a heat sink.

invention Solutions are in the independent claims described. The dependent claims contain advantageous embodiments and modifications of the invention.

at the invention passes through a working fluid, preferably a gas, in particular air, a flow path in one predetermined flow direction. The transport of the working fluid is made by taking advantage of the temperature difference between the Higher temperature located heat source and the lower temperature heat sink accomplished. In the flow path are for this successively at least one first fluid container and downstream of it in the flow direction a second fluid container arranged. The volumes of Fluid containers are provided by valve means along the Flow path completed. The valve devices can for pressure gradient of the working fluid in the direction the predetermined flow direction of the flow path between opened directly consecutive fluid containers become. The pressure of the working fluid in the fluid containers is caused by cyclically alternating action of the heat source or the heat sink varies cyclically, for which in particular Drive devices can be provided. One cycle advantageously comprise at least two sub-cycles, for example in a first subcycle, the pressure of the working fluid in one first fluid container by the action of the heat source increases and the pressure of the working fluid in a second Fluid container under the action of the heat sink decreases and in a second part cycle of the same cycle the pressure of the working fluid in the first fluid container under action reduces the heat sink and in the second fluid container is increased under the action of the heat source, wherein increasing or decreasing the pressure of the working fluid compared to the pressure in the other sub-cycle is. Can increase and decrease the pressure also be distributed inversely to the subcycles. Action of the Heat source means a heat flow from the Heat source, action of the heat sink a heat flow to the heat sink. At least in every cycle once a pressure gradient in the specified flow direction the flow path, which by the in the given Flow direction openable valve devices degraded or at least reduced, with working fluid in the predetermined flow direction, d. H. in the flow path is transported downstream.

advantageously, The pressure of the working fluid is thereby along the flow path elevated. Preferably, the working fluid at the exit of the last Fluid container fed to a pressure reservoir, from which it can be removed for various purposes is. As a working fluid can advantageously air, if necessary be used after prior filtering and / or cleaning. In particular, the working fluid motors, for. B. pneumatic motors drive, which when coupled with generators electrical power generate or otherwise serve as drives. compressed Air can also be used for many types known per se Compressed air applications, can also be used in pneumatic tools.

In another embodiment, the invention with the effect of Generation of a pressure difference of the working fluid between inlet and output also be used at the input terminal or the associated with this fluid source a negative pressure to generate the ambient pressure.

For the action of the heat source to increase the pressure or the heat sink to reduce the pressure, a displacement fluid, preferably a gas is preferably used at substantially constant container volume in the fluid containers, which absorbs when exposed to the heat source from this heat and the action of the Heat sink gives off to this heat.

In first advantageous embodiment, the displacement fluid be given by the working fluid itself, which in heat absorption undergoes a pressure increase and in the flow direction of the Flow path to the downstream adjacent Fluidbhälter in these expands or at heat release a pressure reduction learns and from the upstream adjacent Fluid container working fluid through the arranged between these valve means can flow.

In Other advantageous embodiments include the fluid container in a by a movable partition, in particular a flexible Membrane separated partial volume of a separate from the working fluid Displacement fluid, which on absorption of heat the heat source increases pressure and volume and for that in the remaining subvolume of the assumed constant the entire container volume working fluid located Reduces volume and increases the pressure and working fluid at least partially displaced in the downstream adjacent fluid container. In a similar manner, when heat is released the positive displacement fluid to the heat sink pressure and Reduces the volume of separated displacement fluid and thereby increasing the volume of the working fluid and the pressure is reduced so that working fluid via valve means of an upstream adjacent fluid container can flow.

advantageously, are more than two fluid containers each with interposition provided by valve means along the flow path, so that between a first fluid container at the entrance the flow path and your last fluid container at the exit of the flow path at least one, preferably a plurality of intermediate fluid containers in the course of the flow path are arranged. Advantageously, fluid containers follow Influence of the heat source on the one hand and fluid container with the action of the heat sink on the other hand, respectively within a subcycle alternately, preferably each every second fluid container under the action of the heat source and the others under the action of the heat sink stand and the action of heat source or heat sink reverses in the next part cycle. Especially with strong uneven heat transfer from the heat sink and the heat source to the Displacement fluid or working fluid and / or at more uniform Rotary movement of the containers can also be more than be provided two sub-cycles.

The in the course of the flow path immediately consecutive Containers are thermally insulated from each other. Also a Heat transfer through the valve devices, with the exception of a desired flow of working fluid in the direction of a pressure gradient, negligible low.

The Fluid containers are advantageously by segments, which occupy separate angular ranges about an axis of rotation, of at least one, preferably a plurality of rotatable bodies, in particular Roll bodies, formed. Without limitation of Generality is below the execution of the rotatable Body as roll body as preferred, being basically, unless by special circumstances excluded, the versions also on other forms rotatable body should be applicable. The roll body are below as a cylindrical body designated.

In preferred embodiment includes a roller body exactly two fluid containers. The roll bodies are rotatable about an axis of rotation which coincides with the roller axis, wherein the rotation oscillates between two rotational end positions or in a direction of rotation can be cyclically continued. At the between two rotary end positions oscillating rotation are the two rotational end positions advantageously at least 120 °, preferably at least 150 °, in particular approximately 180 ° to each other offset around the axis of rotation. The rotation is advantageously carried out in a temporally shorter section of a subcycle and the rotatable bodies linger over a temporal longer section of a subcycle in a dwell position with maximum possible thermal contact with the heat source or sink. Especially with more than two containers, in particular four fluid containers per rotatable roller body and in a direction of cyclically continued rotation may also be a even continuous rotation of advantage be, in which an acceleration and deceleration of the rotatable roller body is minimized.

advantageously, are several rotatable bodies in preferably synchronous Rotation coupled and fluid lines, in particular with valve devices, interconnected.

In a first advantageous embodiment, a plurality of rotatable, in particular cylindrical bodies can be arranged successively coaxially with each other in the direction of their common axis of rotation and preferably fixed in a fixed mutual position relative to a common shaft on this. The valve means between the individual fluid containers can be arranged in a first advantageous embodiment in a common hollow shaft. In another advantageous embodiment, the valve means may be arranged on the outer circumference of the rotatable bodies. In yet another embodiment, the valve means axially ge conditions the group of rotatable bodies and offset against heat source and / or heat sink to be arranged.

In another advantageous embodiment may have several rotatable, in particular cylindrical body with a plurality of containers transversely to their respective axes of rotation, in particular with parallel aligned axes of rotation, relative to each other be arranged offset and in particular a flat or an annular Form a group. Fluid lines with valve devices which the several rotatable body or contained therein Connect fluid container, are doing advantageously axially against the fluid container and the heat source and heat sink offset.

at a device with a plurality of containers can this in a serial arrangement a single continuous Path, in other execution but also several parallel ones Form paths or a branched path structure. In particular, can also be provided, fluid lines and valve assemblies at inputs and outputs of the plurality of containers shape so that between a single flow path or multiple parallel flow paths or a branched one Path structure can be switched flexibly. In particular thereby with a device generating different output pressures and / or an adaptation to the withdrawal rate advantageously possible.

Between in a flow path of successive containers Can cache for the Be inserted working fluid.

The Heat source is advantageously through a chamber, which the fluid containers or the rotatable, containing them especially cylindrical body surrounds and is preferably adapted to the shape of the fluid container, with a liquid or gaseous medium as Formed heat transfer medium. In special execution, especially for the utilization of solar radiation, the heat source can also contain a radiation absorber.

The Heat sink can advantageously be a gaseous or contain liquid medium as heat carrier, which analogous to the heat source in a fluid container surrounding chamber may be included.

liquid and / or gaseous media as a heat transfer medium from heat source and / or heat sink can promoted relative to the fluid container, for. B. pumped through a chamber surrounding the fluid container so that cooled medium is the heat source dissipated and replaced by warmer or heated Medium of the heat sink dissipated and by colder be replaced. The flow of the or the heat transfer medium can advantageously as a drive power for the drive means or used as part of such drive power.

In Particularly advantageous embodiment is of the two heat carriers from heat source or heat sink of a liquid and a gaseous, preferably the liquid Heat carrier through water and gaseous Heat carrier formed by air and / or water vapor is.

In particularly advantageous embodiment can substantially without affecting the successive cycles subsequent transport of the working gas pressure differences, which in Change between successive sub-cycles exist, exploited be to drive energy or part of it when switching between to win the subcycles. This can also be a mechanical buffering of drive energy, in particular in one or more separate Be provided fluid containers.

The The invention is based on preferred embodiments illustrated in detail with reference to the figures. there shows:

1 a first advantageous embodiment in an oblique view,

2 a variant too 1 in a cutaway view,

3 the arrangement after 2 in a second subcycle,

4 a sectional view too 2 with view in the axial direction,

5 an embodiment with container membranes in an oblique view,

6 a version with three containers per roller body,

7 an arrangement with several flow paths and external valves,

8th Details of a coupling ring 7 .

9 an arrangement with axially separate from the heat transfer valve device,

10 an example of a bi-metal drive,

11 a version with an annular An order of containers,

12 an embodiment for the utilization of radiant heat,

13 an example of a valve assembly to 12 .

14 a form of recovery of drive energy for the device.

1 shows an oblique view of a device for obtaining mechanical energy in the form of a compressed working fluid AF, which is supplied from a fluid source FQ a flow path via an input valve VE and discharged via an output valve VA to a fluid sink FS. When using air as working fluid AF, the fluid source FQ can be, in particular, the ambient air which is supplied to the flow path, optionally after filtering and / or cleaning. The fluid sink may be any type of working device that is operable by the fluid. In the case of using a gas or in particular air as fluid, the fluid sink FS may in particular contain a compressed gas storage, which is charged by the device with working fluid and increased pressure and from which the working fluid under elevated pressure for mechanical work can be removed.

The device after 1 contains two cylindrical bodies WA1 and WA2, which are arranged on a common shaft WE and are rotatable with this synchronously about a rotation axis DA. The rotation can either be done alternately in opposite directions or continued in the same direction of rotation. A double arrow on the left side of the figure symbolizes the alternating rotation of the two roller bodies WA1, WA2. The direction of the axis of rotation DA should be referred to as the axial direction AR.

Everyone the two roller body WA1, WA2 is characterized by a heat insulating internal partition BI divided into two containers, wherein the partitions BI, which are the container of a roll body separate from each other, for both roll body in the same rotational position with respect to the axis of rotation DA or the shaft WE are aligned.

The first roller body WA1 contains a first container B1 and a second container B2, which are connected to one another via a fluid line FL with a valve V12. The second roller body WA2 contains a third container B3 and a fourth container B4, which are connected via a fluid line FL to a valve V34. The second container B2 in the first roll body WA1 and the third container B3 in the second roll body WA2 are connected to each other via a fluid line with a valve V23. The first container B1 is further connected via a fluid line FL and an input valve VE with an input line EL, via which the working fluid AF can be supplied to the flow path. The fourth container B4, which in the sketched example is the last container in the course of the flow path, is connected via a fluid line to an outlet valve VA with an outlet line AL leading to the fluid sink FS. The flow path for the working fluid is given by the input line EL, the input valve VE, the first container B1, the valve V12, the second container B2, the valve V23, the third container B3, the valve V34, the fourth container B4, the Output valve VA and the output line AL and a plurality of not individually designated fluid lines FL. The arrangement of the fluid lines FL and the valves VE is to be understood schematically and is intended to illustrate only the basic structure. In the real case, the valves and the fluid lines are preferably arranged elsewhere, which is illustrated by different examples. The roller bodies are in an in 1 arranged for the sake of clarity not with marked means containing a cold ambient volume with a located at a lower temperature TL heat transfer medium WL and a second partial volume with a located at a higher temperature TH heat transfer medium WH. The heat transfer media are hereinafter also referred to simply as heat transfer. In particular, for the heat carrier located at the higher temperature TH, the volume around the roller bodies is advantageously adapted to their shape with a small volume difference. The ambient volume with the colder heat carrier WL can also be adapted to the roll shape or be larger or even completely open. Preferably, one of the heat transfer medium is liquid and the other is gaseous. For example, the heat carrier WH at a higher temperature TH may be formed by water vapor or hot air and the colder heat carrier WL may be formed at the temperature TL by cooling water. When using a gaseous and a liquid heat carrier, a particularly simple separation of the two ambient volumes through the surface of the liquid heat carrier is given and an advantageous thermal sealing of the two ambient volumes can be done in a simple manner by a seal on the surface of the liquid heat carrier, which also floating can rest on the liquid heat carrier.

The dividing walls BI within the cylindrical bodies advantageously pass through the axis of rotation DA and subdivide the cylindrical bodies into equal partial volumes as containers B1 to B4. The successive in the axial direction AR cylindrical bodies may also have different dimensions in the axial direction or in the radial direction with respect to the axis of rotation. Preferably, however, all container volumes are the same size. The container volumes of the cylindrical bodies which are assigned to the environmental volumes are advantageously highly thermally conductive in order to ensure good heat transfer between the heat transfer media and the working fluid AF contained in the containers B1 to B4. The roller-shaped bodies can be separated in the axial direction AR, as shown, or also directly adjoining one another. A thermal insulation in the axial direction is not required because the arranged in the axial direction in each case aligned to one another containers are always surrounded by the same heat transfer medium, ie in the outlined position, the container B1 and B3 in thermal contact with the cold heat carrier WL and the container B2 and B4 are in thermal contact with the warm heat transfer medium WH.

In operation of the device, the cylindrical bodies of the device are after 1 advantageously rotated during short movement phases between two mutually offset by 180 ° rotational end positions and linger over a longer relative to the rotational movement period in each one of the two end positions.

The Valves VE, V12, V23, V34 and VA each have a preset value Forward direction and lock in the other direction. This can be given by the fact that the valves as check valves are executed and pressure gradient only in the for the flow path provided flow direction from the input line EL to the output line AL by opening Balancing the valves, on the other hand pressure gradient opposite this flow direction by locking the valves upright receive. The valves can be individually or all as well be executed controllable valves, the controller by control means not shown, for example mechanically, electrically or magnetically and opening the valves in time depending on rotational movement and rotational position This is done so that pressure gradient in the flow direction of the flow path balanced and pressure gradient against the flow direction of the flow path be maintained.

The invention makes use of the fact that a fluid expands when heated and contracts on cooling or, at a constant volume, the pressure of the fluid increases when heated and decreases on cooling. A heating of the fluid is effected by the action of a heat source, which is given by the heat carrier located at the higher temperature TH WH, a cooling of the fluid is effected by the action of a heat sink, which is given by the located at the lower temperature TL heat transfer medium WL. At the in 1 sketched arrangement, the working fluid AF is at the same time a change of temperature, pressure and volume experienced positive displacement fluid, which act on the heat transfer of heat source or heat sink on the well-heat-conducting container walls. In another embodiment, a separate displacement fluid may be provided, which act on the heat sink and heat source and which undergoes a corresponding change in volume and / or pressure change in temperature change and this transfers to the working fluid located in the flow path.

In the in 1 outlined position of the device with the containers B1 and B3 under the action of the heat sink, which is formed by the lower temperature located cold heat carrier WL, and the containers B2 and B4 under the action of the heat source, which is located at the higher temperature TH warm heat carrier WH is formed, takes the working fluid AF in the containers B1 and B3 during the residence time in this position, a lower temperature, in particular substantially the temperature TL of the heat sink in the containers B2 and B4 a higher temperature, in particular substantially the temperature TH of the heat source one. In principle, the temperature of the working fluid may also be between upper and lower temperature values, which deviate more strongly from the temperatures of the heat source and the heat sink, as a result of which the cycle time can be shortened. However, the compression of the working fluid per duty cycle is more effective with greater temperature variation of the working fluid. Advantageously, the highest TAmax and the lowest TAmin temperature of the working fluid (or a Verdrängerfuids) by a maximum of 20%, in particular at most 10% of the temperature difference of heat source and heat sink of these different, (TAmin-TL) ≤ (TH-TL) 0, 2 (or 0.1), (TH-TAmax) ≤ (TH-TL) 0.2 (or 0.1).

An equivalent arrangement illustrating the sequence of duty cycles in two subcycles is shown in FIG 2 and 3 shown as a sectional view with a running through the axis of rotation DA vertical cutting plane. Also indicated here are a volume limitation by a chamber KL of the surrounding volume with the colder heat carrier WL and a volume limitation by a chamber KH for the warmer ambient volume with the warmer heat carrier WH.

The containers are at the in 2 and 3 sketched device arranged on a hollow shaft WV, within which the valves are housed. The folks in the flow path container and the valves are in 2 and 3 provided with the same names as the tanks and valves in 1 , 2 , shows the rotational position of the device in the 1 equivalent position. 3 shows a rotated by 180 ° against the axis of rotation DA position of the container, including valves in the hollow shaft WV. Insofar as the valves are controllable valves, they may conveniently be actuated mechanically within the hollow shaft with slides or traction means running in the direction of the axis of rotation or electrically, in each case advantageously by control devices offset laterally against the cylindrical bodies and the environmental volumes.

When Working fluid and, if present separately, positive displacement fluid in the following a gas, in particular air understood. synonym to working fluid is therefore also the term working gas in the following second hand. It is assumed that the maximum temperature of the working fluid TAmax approximately equal to TH, the minimum temperature TAmin is about equal to TL. The explanations apply analogously for TAmax, TAmin instead of TH, TL, if the former are more different from the latter.

In the in 1 and 2 shown rotational position of the device, which is taken in a first of two part cycles of a working cycle of the device and maintained for a residence time, the gaseous working fluid AF is in the containers B1 and B3 towards the end of the residence time substantially at the lower temperature TL and the working gas in the containers B2 and B4 substantially at the higher temperature TH corresponding to the temperatures of the containers respectively surrounding different heat carrier WL and WH. During the cooling of the working gas in the container B1 and the associated reduction of pressure and / or volume of the working gas flows via the input valve VE working gas from the fluid source FQ, so that in the container B1, the fluid at the temperature TL and a pressure P1L located. The pressure P1L is substantially equal to the pressure PQ of the working gas in the fluid source FQ, which flows on the inlet valve VE at the pressure reduction occurring in the container B1 by cooling. If the input valve VE is a controlled valve, this is preferably only at the end of the subcycle, in which the container B1 is in the cold heat carrier WL, opened to reliably prevent backflow of working gas from the container B1 to the fluid source. The gas amount of the working gas in the container B1 at the pressure P1L (= PQ) and the temperature TL is denoted by M1L.

in the Container B3 rises during the cooling of the Working gas a pressure P3L, wherein when the pressure drops P31 in the container B3 under the pressure P2H in the container B2 working fluid from the container B2 via the valve V23 is poured into tank B3 until the gas pressures in the containers are again substantially equalized are. A stream of working fluid in the opposite direction from the container B3 to the tank B2 is prevented by the valve V23. The Gas volume in tank B3 at the end of the dwell time of the first Subcycle is called M3L.

In the container B2, which is under the action of the heat source with the temperature TH, the working gas at the end of the residence time in this position substantially assumes the temperature TH of the heat carrier WH. The container B2 was in the second part cycle of the previous cycle at the position of the container B1 and contained when ingested in 2 initially sketched a gas quantity equal to M1L with the temperature TL and the pressure P1L.

By heating the working gas in the container B2 during the residence in the in 2 sketched position under the action of the heat source on the container B2 and the working gas located in this working gas takes substantially the higher temperature TH, wherein upon heating and cooling, respectively, the container volume was assumed to be constant. By heating the working gas in the container B2, the pressure of the working gas in the container B2 increases. A resulting pressure gradient opposite to the flow direction from the container B2 to the container B1 is maintained by the valve V12 blocking in this direction. A pressure gradient in the flow direction between the container B2 and the downstream container B3 is compensated by the valve V23, wherein working fluid flows from the container B2 via the valve V23 into the container B3 until the pressure gradient from B2 to B3 is substantially balanced. The working fluid flowing from the container B2 into the container B3 is simultaneously cooled again in the container B3 to the lower temperature. The valve V23 can be opened toward the end of the residence time of the position outlined, but is preferably opened over the predominant or, in particular, substantially complete period of the residence time of the device in the position outlined. Towards the end of the residence time of the device in the in 2 sketched position thus sets in the container B2 a fluid quantity M2H at the temperature TH and in the container B3 a fluid quantity M3L at the temperature TL, the pressures P2H in the container B2 and P31 in the container B3 being compensated by the valve V23. Due to the different temperatures TH and TL, the amount of gas M2H in the container B2 is lower than in the container B3. The fluid pressure P2H = P3L in the tanks B2 and B3 is higher than in the tank B1.

The heating of the working fluid AF in Be container B4 in the 2 sketched position causes for the amount of gas in this container, which was in the second part cycle of the previous cycle under the action of the heat sink with the colder heat carrier WL and therefore at the beginning of the subcycle with in 2 sketched position, the amount of fluid M3L contains an increase in pressure and temperature of the working gas, the adjusting thereby adjusting higher pressure P4H in the container B4 via the output valve VA to the final pressure PS in a presumed as a fluid sink FS gas pressure tank DB and is limited to this. As the fluid pressure P4H in the reservoir B4 rises above the outlet pressure PS in the fluid sink FS, fluid therefore flows from the reservoir B4 in the direction of the downstream pressure gradient via the outlet valve VA into the fluid sink. A pressure difference between the pressure P4H in the container B4 and the opposite to the flow direction, ie arranged upstream of the flow path Behäl ter B3 with the fluid pressure P3L remains maintained because of the blocking action of the valve V34.

At the end of the position 2 Represented first part cycle of a working cycle of the device, the container B1 to B4 with the hollow shaft WV and the valves about the axis of rotation DA in a in 3 rotated position in which, during the residence time of a second part cycle of a working cycle of the first container B1 and the third container B3 under the action of the heat source with the heat carrier WH and the second container B2 and the fourth container B4 under the action of the heat sink with the colder Heat carrier WL are located. By heating the working fluid in the container B1 to the temperature TH increases in the container B1, the pressure of the working fluid from P1L previously to a higher value P1H, wherein a resulting pressure gradient is maintained upstream against the pressure PQ of the fluid source FQ due to the blocking effect of the valve VE , At the same time, in the container B3, with the heating of the working fluid to the temperature TH in this container, the pressure of previously P3L rises to a higher value P3H.

in the Container B2 drops on cooling of the working fluid to the temperature TL the pressure in this tank of previously P2H (= P3L) to a lower value P2L and in the container B4 drops as the working fluid cools, the pressure in this Container from previously P4H to a lower value P4L. A pressure gradient occurring during the temperature change between the container B3 and the container B2 upstream the predetermined flow direction of the flow path is maintained by the blocking effect of valve V23. Also maintains a pressure gradient between the outlet pressure PS of the pressure vessel of the fluid sink and the upstream container B4 due the blocking effect of the valve VA.

The pressure P1H rising in the container B1 during the heating of the working fluid and the pressure P2L sinking in the container B2 due to cooling of the working fluid is compensated by the valve V12 for a pressure gradient from B1 to B2, so that at the end of the second partial cycle of one working cycle the pressures P1H and P2L in the containers B1 and B2 are substantially equal. Correspondingly, between the container B3 and the container B4, a balance of the pressure P3H rising in the container B3 and the pressure P4L sinking in the container B4 takes place via the valve V34, so that P3H = P4L at the end of the second partial cycle. It thus finds the in 3 sketched second part cycle of a working cycle an overflow of working fluid from the container B1 into the container B2 and from the container B3 into the container B4, respectively in a predetermined flow direction of the flow path instead, so that in the containers B1 to B4 to each of these drawn fluid quantities M1H, M2L, M3H, M4L, and because of the balanced pressures between B1 and B2 or between B3 and B4 and the different temperatures of the pressure-balanced containers, the quantities M1H <M2L and M3H <M4L.

After the residence time of the device in the 3 sketched position of the second part cycle of a work cycle begins a new work cycle, wherein the device in a time-short movement section of the first part cycle of the new work cycle in the in 2 sketched position is rotated and dwell for a dwell over a longer time relative to the movement portion of the first part cycle in this position. At the end of the stay they are already increasing 2 described during the first part cycle of the new working cycle working fluid flows from the fluid source into the container B1, from the container B2 into the container B3 and from the container B4 in the fluid sink described temperature, pressure and quantitative ratios of the working fluid in the various containers.

The assignment of 2 to a first subcycle and the 3 to a second subcycle is arbitrary because of the cyclic operation and may be the other way around. The duration of a working cycle or the sub-cycles can be specified independently of the temperature values fixed or by temperature-independent parameters, eg. B. as a time value in a control device. A change between two successive partial cycles can also be dependent on temperature values or temperature differences, pressure values or pressure differences, for which, for. B. temperature and / or pressure sensors can be arranged in the device.

4 shows with a view in the axial direction of the axis of rotation DA a section through an arrangement 3 with containers B1 and B2 as well as the valves VE and V23 connecting the containers with each other and with the fluid source or the following container within the hollow shaft WV.

implied In addition, there is a boundary KH of the roll body WA1 surrounding and adapted by a vault Limitation KH of an ambient volume for a warm heat transfer medium WH and a further limitation KL, which in an analogous way the Roller body WA1 surrounds below and also this through Semicircular curvature adapted in the form is and an ambient volume for a cold heat carrier WL limited. The ambient volumes for the warm heat carrier WH and the cold heat carrier WL are through insulation bodies KI separated, these isolation body with a liquid cold heat carrier WL and a gaseous warm heat carrier WH advantageously also designed as a floating body could be. The insulator KI between the two Ambient volumes effect advantageously that no direct Heat transfer between the two heat carriers WH and WL and in particular no condensation of an example steam formed by warm heat carrier WH on the surface of a cold heat carrier formed by water WL can be done.

5 indicates in 1 Analogous view with the same name of the valves, a device in which in two roll bodies WT1, WT2 turn working gas volumes BA1, BA2, BA3 and BA4 in the to the containers B1 to B4 in 1 with the introduction of fluid lines with valves to a flow path for a working fluid AF between a fluid source FQ and a fluid sink FS are joined together. The working fluid volumes BA1, BA2 and BA3, BA4 of the cylindrical bodies are separated by partitions BI.

Unlike the arrangement after 1 are in the arrangement after 5 the half-spaces of the cylindrical bodies WT1, WT2 formed by the dividing walls BI are not completely occupied by the working gas AF but divided by flexible membranes ME1, ME2, ME3 and ME4. The volumes of the half-spaces formed by the dividing walls BI in the roll bodies are assumed to be the same size and substantially independent of temperature. The membrane ME1 separates in a first half-space of the roll body WT1 whose half-space volume into a partial volume BA1 for the working fluid and a partial volume BV1 for a displacement fluid, wherein the two sub-volumes BA1 and BV1 are variable, but in the sum constant. In a corresponding manner, the membrane ME2 divides the further half space of the first roll body into a partial volume BA2 for the working fluid and a partial volume BV2 for a positive displacement fluid. The second roll body WT2 is assumed to be constructed as equal to the roll body WT1, wherein a membrane ME3 divides a first half-space into a partial volume BA3 for the working fluid and a partial volume BV3 for a displacement fluid and a membrane ME4 divides the second half-space into a partial volume BA4 subdivides the working fluid and a partial volume BV4 for a positive displacement fluid, wherein working fluid and positive displacement fluid in the adjacent partial volumes are separated from each other by the membranes.

The Heat source with the temperature TH and the heat sink with the temperature TL act on the displacer in the respective sub-volumes BV1, BV2, BV3, BV4 and cause upon heating of the displacement fluid an increase of pressure and volume, upon cooling of the displacement one Reduction of pressure and volume of the displacement fluid. Transmitted by the flexibility of the membranes ME1 to ME4 the fluid pressures of the displacement fluid in the partial volumes occupied by the displacer fluid, respectively on the working fluid in the over the membranes respectively adjacent sub-volumes BA1 to BA4 of the working fluid.

In the example below 5 Both the partial volumes BV1 to BV4 of the displacement fluid and the partial volumes BA1 to BA4 of the working fluid are in contact with the heat carriers WH and WL of the heat source and the heat sink, respectively. In particular, the thermal contact between partial volumes BV1 to BV4 of the displacement fluid to heat source or heat sink is essential. The thermal contact of the heat source or heat sink with the partial volumes of the working fluid is, on the other hand, subordinate.

A device with subdivision of spaces of constant volume into partial volumes for working fluid and displacing fluid by means of displaceable parting surfaces, in particular flexible membranes is particularly advantageous if the displacing fluid between the state at the temperature TL and the state at the temperature TH a much larger change of volume and / or pressure indicates as the working fluid. This may in particular be the case if the displacement fluid is selected so that between the temperatures TL and TH not only an expansion of the fluid takes place in an aggregate state, but if the displacement fluid simultaneously evaporates between the two states when heated or when cooled in the liquid phase condenses. Since the pressure conditions in the individual sub-volumes are different, in particular the pressure along the flow path increases, different amounts can be present in the individual sub-volumes BV1 to BV4 for the displacing fluid Be provided amounts of displacement fluid and / or different displacement fluids or mixtures.

The operation of the device after 5 is equivalent to the mode of action of 1 with the essential difference that the displacement fluid is not transported further and remains in the individual sub-volumes.

In 6 is in too 4 an analogous view sketched an embodiment in which a rotationally symmetrical roll body WKD is divided about the axis of rotation DA into three segments whose volumes are constant and preferably equal to each other. The segments are in too 5 corresponding manner divided by means of flexible membranes ME61, ME62 and ME63 in partial volumes A61, A62, A63 for a working fluid and G61, G62, G63 for a Verdrängerfluid. The working fluid partial volume A61 of a first segment K61 is connected via a valve V612 to the working fluid partial volume A62 of the segment K62, wherein the connection is unidirectionally directed from the working fluid partial volume A61 to the working fluid partial volume A62 and blocks the valve in the opposite direction. The working fluid partial volume A62 is connected via a valve V623 to the working fluid partial volume A63 of the segment K63, wherein again the valve V623 permits a flow of working fluid only from the partial volume A62 into the partial volume A63. Working fluid can flow from a fluid source or from a working fluid partial volume lying in the course of a flow path in front of the partial volume A61 into the partial volume A61 via a valve VDE. A fluid flow in the opposite direction is blocked by the valve VDE. From the working fluid partial volume A63, working fluid can flow via a valve VDA to an outlet line or a working fluid partial volume following in the flow path. The valve VDE blocks a flow of working fluid in the opposite direction into the sub-volume A63.

In the in 6 sketched device is assumed as a heat sink with the temperature TH a liquid, such as warm or hot water. As a heat sink, a gaseous medium, in particular ambient air with the lower temperature TL is assumed. The displacement fluid partial volume G62 is in good thermal contact with the liquid warm heat carrier of the heat source via the wall of the segment K62, so that the displacement fluid in the partial volume G62 expands and correspondingly restricts the partial volume A62 for the working fluid. In this case, working fluid from the partial volume A62 is displaced via the valve V623 into the working fluid partial volume A63. A displacement of working fluid from the sub-volume A62 in the, relative to the predetermined flow direction of a flow path through all working fluid sub-volumes, upstream partial volume A61 is prevented by the valve V612.

The cylindrical body WKD is progressively moved incrementally in 120 ° steps in a clockwise direction corresponding to three subcycles of a working cycle in one direction of rotation. The segment K61, which was under the action of the heat source in the previous subcycle, is now in the 6 sketched position in thermal contact with the heat sink, wherein the pressure and volume of the displacement fluid in the partial volume G61 decrease relative to the state of the displacement fluid in the partial volume G62. In this case, working fluid flows via the valve VDE into the increasing partial volume A61.

The Device with more than two segments in mutual angular offset around the axis of rotation is particularly advantageous if the heat balance between the displacer fluid and the heat source is much more intense than the heat exchange between the displacer fluid and the heat sink, so that as indicated by the course of the membranes, the displacement fluid while under the action of the heat source, although quickly on approximately heats the temperature TH of the heat source, for cooling to the temperature TL below However, the heat sink requires a longer period of time. In the sketched arrangement is the positive displacement fluid for a subcycle within a three-part work cycle under the action of the heat source, but over two sub-cycles of a work cycle under the action of the heat sink.

By the different course of membranes ME61 and ME63 is indicated, that the displacer fluid during a subcycle in the position of the segment K61 only to an intermediate temperature cools and thereby only a medium pressure achieved and only in a further subcycle according to the Position of segment K63 continues to cool and one more time significantly reduced partial volume G63 with correspondingly lower Pressure takes and a particularly large partial volume A63 for the working fluid.

Upon further rotation of the roller body WKD clockwise by 120 ° corresponding to the transition to a next part cycle is done by increasing the temperature, pressure and volume of the displacement of the small part volume G63 in a large part volume according to G63 6 a strong reduction of the previously large partial volume A63 of the working fluid into a small partial volume according to A62 6 and associated therewith effective displacement of working fluid in the flow direction of the flow path.

Instead of the connection of segments, containers or partial volumes of the working fluid within a cylindrical body with each other can also be provided that a plurality of parallel flow paths are formed and containers are mainly or exclusively connected in the axial direction. For example, in the arrangement according to 1 or 2 . 3 be provided that a first flow path via a first inlet valve to the first container B1 and via a unidirectional valve to the container B4 and from there to a first output valve and a second flow path from a second inlet valve to the container B2 and via another unidirectional valve to the container B3 and from there to another output valve leads. In a similar manner, in an arrangement according to 6 be provided that a plurality of roller bodies are arranged one behind the other and that working fluid sub-volumes in 120 ° about the axis of rotation offset from each other segments of axially successive roller bodies via unidirectional valves are interconnected.

A subdivision into z. B. three segments about the axis of rotation DA within a roller body may be useful in the same way, if the heat transfer between the displacement fluid and a warmer heat transfer is slower than between the positive displacement fluid and a colder heat transfer medium, in which case the warmer heat transfer medium as a heat source over a longer Period, in particular more sub-cycles acts on the displacement fluid than the heat sink with the colder heat transfer medium. The operation of the arrangement according to 6 is of course, with the exception of the transition liquid-gaseous completely equivalent in the case that the individual segments are not divided into partial volumes for working fluid and positive displacement fluid, but the chambers are each completely filled with the working fluid.

7 shows a further arrangement with a plurality of cylindrical bodies KQ1, KQ2 and KQ3 indicated, which are rotatable together about a rotational axis DA in a rotational direction DR and turn through environmental volumes with a warm heat carrier WH and a cold heat carrier WL. The cylindrical bodies are in this case divided into four mutually offset by 90 ° to each other aligned chambers, which are partitioned from each other by heat-insulating partitions BI. The chambers of the first cylindrical body KQ1 are referred to as containers B11, B21, B31 and B41, and those of the second cylindrical body KQ2 as containers B12, B22, B32 and B42. The containers of these and possibly further in the axial direction following roll body are arranged in four parallel flow paths, wherein a first flow path, the container B11, B12, ... and a second flow path, the container B21, B22, ... and a third flow path, the container B31, B32, ... and a fourth flow path containing the containers B41, B42, .... Associated with each flow path is an inlet valve VE11 or VE21 or VE31 or VE41 associated with the associated container of the first cylindrical body, via which working fluid can be introduced from a fluid source into the container of the first roller body. A forwarding of working fluid between successive roll bodies in the axial direction and the respective individual flow paths associated containers via other valves. A shift of working fluid between two containers one and the same roller body does not take place.

For the forwarding of working fluid between successive containers one and the same flow path can be used in the simplest design check valves. 7 shows in conjunction with 8th a particularly advantageous arrangement using switchable valves and coupling rings between in the axial direction AR successive roll bodies. Shown are a first intermediate ring KR12 between the first roller body KQ1 and the second roller body KQ2 and a second intermediate ring KR2 between the second roller body KQ2 and the indicated third roller body KQ3. The valves between the rolling bodies following one another in the axial direction can in particular be connected to and / or integrated into these intermediate rings.

The belonging to a flow path container are advantageously arranged in successive roll bodies offset by 180 ° from each other, as in 7 entered.

In 8th is sketched an example of the intermediate ring KR12 between the cylindrical body KQ1 and the following in the axial direction roll body KQ2 an advantageous construction of a valve assembly with such an intermediate ring.

The intermediate ring contains an annular channel RK, to which a plurality of valves with a one-sided valve connection is connected. The respective other connections of the individual valves are connected to individual containers of the first cylindrical body KQ1 or of the second cylindrical body KQ2. The valves are designed as switchable valves, which are closed in an idle state and are opened by a targeted operation. According to the sketch after 8th is such an operation in the form of a mechanical actuation by means of stop members AE and AA seen before. There are each switchable valves as valves between the individual containers the roller-shaped body KQ1 to the annular channel RK of the intermediate ring KR12 and further switchable valves are provided as valve connections between the annular channel RK and individual containers of the cylindrical body KQ2.

Of the first flow path passes through a first inlet valve VE11, the container B11, a valve VA11, the annular channel RK, a valve VE12, the container B12, a switching valve VA12 etc. progressing in the axial direction. Run accordingly the second flow path via an inlet valve VE21, the container B21, a valve VA21, the annular channel RK, a valve VE22, the container B22, a switching valve VA22 etc., the third flow path via an inlet valve VE31, the container B31, a valve VA31, the annular channel RK, a Valve VE32, the tank B32, a valve VA32 etc. and the fourth flow path via an inlet valve VE41, the container B41, a valve VA41, the annular channel RK, a valve VE42, the container B42, a valve VA42 etc.

The rotation of the rotatably connected to each other and with the intermediate rings roller body can be carried out in successive sub-cycles stepwise by 90 ° or continuously. Due to the 90 ° division of the roll body into four containers, a generally sufficient period of time for the heat exchange of the working fluid in the individual containers with the heat source or the heat sink results even with continuous further rotation. The actuation of the valves can with continuous rotation of the roll body group about the axis of rotation to short sections when passing through switching positions, such as in 8th shown to be limited. In particular, with gradual further rotation of the roller body assembly about the axis of rotation by 90 ° each affected valves remain open over the residence time in a position away, for which the 8th in the same way explanatory serves. Finally, in other embodiments of the mechanical actuation, in the case of magnetic and / or electrical actuation of the valves, possibly using an electric control device and / or electromagnetic actuation means, the valves may also be opened longer or shorter independently of the continuous or incremental rotation.

The positions of each valve in 7 and 8th is primarily chosen to illustrate the proposed operation of such an arrangement, without it being understood that a binding to such an arrangement. In particular, the valves can be analogous to 2 also be arranged within a hollow shaft.

The valves VA11, VA21, VA31 and VA41 leading from the individual containers B11, B21, B31, B41 of the roller body KQ1 in the predetermined flow direction of the flow paths to the annular channel are opposite to those from the annular channel RK of the intermediate body KR12 to the individual containers B12, B22, B32, B42 of the following in the axial direction roller body KQ2 leading valves VE12, VE22, VE32, VE42 offset both axially and circumferentially offset by a small amount, but this serves primarily to illustrate the operation. In the 8th Registered mechanical, fixed switching stops AE and AA are accordingly perpendicular to the plane of the 8th arranged offset from one another. The switching stop AA actuates exclusively the valves VA11, VA21, VA31 and VA41, whereas the switching stop AE actuates exclusively the valves VE12, VE22, VE32 and VE42.

In 8th are in the area surrounded by the annular channel still registered the names of the perpendicular to the drawing plane before or behind the intermediate ring KR12 container. At the not connected to the annular channel connection lines of the individual valves also associated with this line sections container designations are attached.

In the in 8th sketched rotational position of the intermediate ring KR12, the direction of rotation is carried out together with the roller bodies in the clockwise direction, the working fluid in the containers B11 and B32 is heated by the action of the warm heat transfer WH of the heat source, in particular approximately to the temperature TH of the heat carrier WH. The working gas in the containers B31 and B12 is cooled by the action of the cold heat carrier WL of the heat sink, in particular substantially to the lower temperature TL of the cold heat carrier WL. By simultaneously opening the valves VA11 at the stop AA and VE12 at the stop AE heated working fluid from the container B11 via the annular channel in the container B12 overflow. All other containers are separated from the annular channel and therefore separated from such fluid flow.

Upon further rotation of the arrangement, the valves VE12 and VA11 are closed again. During the further rotation of the arrangement by 90 °, the valve VA31 passes the stop AE and the valve VE22 the stop AA, without these valves being actuated. When reaching one opposite the 8th 90 ° offset rotational position of the intermediate ring KR12 with the roller bodies are then the valves VA41 at stop AA and VE42 on the stop AE operated and opened and working fluid flows from the heated container B41 via the valve VA41, the annular channel and the valve VE42 to the cooled container B42. In each of the 90 ° offset rotational positions correspond Thus, fluid is transported downstream in each of the four parallel flow paths.

Instead of the annular channel, which in relation to the container volumes should have small volume, can also be provided that under waiver on the annular channel downstream in the respective flow path located outputs of the container of the first cylindrical Body in the intermediate ring about only one Valve with the upstream entrance of the same Flow path associated container in second cylindrical body KQ2 is connected.

In 9 a device is sketched in which a plurality of cylindrical bodies are arranged on a common shaft. The cylindrical bodies are for example constructed as in the device according to 1 each with two containers B1 and B2, B3 and B4, B5 and B6, etc. per cylindrical body and in each case a heat-insulating partition BI between the two containers of a cylindrical body. A separating layer, separating surface or the like between a cold heat carrier WL in a lower portion of the cylindrical bodies and a warm heat carrier WH in an upper portion of the cylindrical bodies is denoted by KI. The upper region of the cylindrical bodies is covered in each case by a shell KH1 or KH2 or KH3, which surround the outer walls of the cylindrical bodies in the region of the warm heat carrier WH at a small distance. The warm heat transfer medium WH is predetermined, for example, as hot steam and introduced via supply lines DL into the space MR around the individual casings KH1, KH2, KH3. The heat transfer from the hot heat carrier WH to the containers of the cylindrical bodies takes place via the volume gap between the casings and the cylindrical bodies, for which purpose this gap can be filled with a gas or a liquid, advantageously with good thermal conductivity. In the case of steam as a hot heat carrier WH, it is advantageously possible to provide a condensate drain line KO for vapor condensed liquid at a low point in the space MR. The sheaths KH1, KH2, KH3 shield the cylindrical bodies against the hot heat carrier WH. In particular, the space MR can thereby be hermetically sealed against the environment and / or the cold heat carrier executed, which is particularly advantageous if the hot heat carrier, for. B. because of contamination with problematic, z. B. radioactive ingredients in a closed system must be performed. The cylindrical bodies are drawn in an intermediate position between two end positions or dwell positions per subcycle of a two-part work cycle.

At the in 9 sketched arrangement no valves are arranged in the area of the cylindrical body or the heat carrier WL and WH. The valves for controlling the flow of working fluid in one or more flow paths are arranged in the axial direction spaced from the cylindrical bodies and the heat carriers, which is represented by a valve group housing VG. The shaft LW contains fluid conduits to and from the individual containers of the cylindrical bodies, and the working fluid passageway passes between containers along a flow path from a reservoir through a conduit of the shaft LW to the valve housing and via valves thereafter back to downstream in the flow path Container. The valve arrangement in the valve housing VG is thereby not subject to any restrictions by the type and temperature of the heat transfer medium or by the structure of the cylindrical bodies or the containers. For example, working fluid is supplied from the valve assembly housing VG via the line L1E integrated into the shaft LW to the first reservoir B1, and from there back to the housing VG via the line L1A in the shaft. After passing through the corresponding valves in the valve assembly in the housing VG, the working fluid flows via the line L2E to the container B2 and from there via the line L2A back to the valve assembly in the housing VG, from there via the line L3E to the container B3 and via the line L3A of this back to the valve assembly in the housing VG, etc. From the valve assembly in the housing VG performs an output line AL to a fluid pressure accumulator DBI. The required for receiving the multiple lines diameter of the shaft LW is not very critical, since the total volume of the container B1, B2, ... is primarily determined by the outer diameter of the cylindrical body because of the quadratic relation and the diameter of the shaft LW contrast is subordinate. The shaft LW may still have a separate sheath BW within a space MR containing the cylindrical body.

Of the Drive for the rotation of the cylindrical bodies can be provided in different ways. It can do this for example, a separate electromechanical and as such easily be provided controllable drive. In another version can be a propulsion of the group of cylindrical bodies from the under higher pressure fluid in the fluid pressure accumulator over a compressed air drive or a similar drive branched off become.

In another preferred embodiment, the drive power or a portion thereof may be using one or, preferably, two drive storage tanks and additional valves associated with the first tank be done as based on 14 exemplified.

14 indicates in 2 and 3 analogous representation of a first stage of a device according to the invention with two containers B1 and B2, wherein in the 2 and 3 described manner, the first container B1 via an input valve VE with a fluid source FQ and a valve assembly V12 is connected to the second container B2, which in turn via a valve assembly V23 with a in 14 not shown third container is connected, etc.

At the in 14 in four steps A, B, C, D of a device shown cycle, the first container B1 in addition via a valve assembly VSH with a subsequently as a drive overpressure fluid reservoir SAH and a further valve assembly VSL with a drive-negative pressure fluid reservoir SAL in combination , The pressure difference of the fluid between SAH and SAL can be exploited to drive a pneumatic drive M which causes rotation of the cylindrical bodies around the axis of rotation DA or at least in conjunction with another drive. Unlike the mark in 2 , and 3 arrows are drawn only on those valves which are open in the step in question. The other, not marked with arrows valves are closed completely or at least in the direction of a pressure gradient as check valves.

Step A after 14 corresponds to the situation 3 , The container B1 is under the action of the heat source, ie on the warm side, the container B2 is under the action of the heat sink, ie on the cold side. The valve V12 is opened to allow working fluid to flow from the container B1 into the container B2. The inlet valve VE locks. The valve assemblies VSL and VSH are closed, so that the fluid reservoirs SAH and SAL are separated from the reservoir volume of the first reservoir B1. At the end of the partial cycle corresponding to the situation after step A, the situation after step B of FIG 14 changed, the valve VSH between the first container B1 and drive overpressure fluid reservoir SAH is opened. Due to the pressure P1H existing in the tank B1 in step A, working fluid flows into the fluid reservoir SAH via the valve VSH, whereby the fluid pressure in the tank B1 decreases to P1LB and the fluid amount in the tank B1 decreases from M1H in step A to M1LB. The valve V12 is closed by a corresponding control or when executed as a check valve due to the pressure gradient from the container B2 to the container B1, so that fluid pressure P2L and fluid amount M2L in the container B2 in step B after 14 remain unchanged. The input valve VE is closed unchanged, as well as the valve VSL. Since no temperature compensation must take place in step B, this step can be short in time.

In the transition from step B to step C after 14 the valve VSH is closed and the assembly rotated by 180 ° about the axis of rotation, so that the container B1 is now under the action of the colder heat sink and the container B2 under the action of the warmer heat source. In the tank B2, the fluid pressure is increased to P2H by the action of the heat source, and working fluid flows through the valve V23 into the third tank not drawn with the amount of fluid in the tank B2 decreasing to M2H.

in the Container B1 cools the working fluid under the action the colder heat sink, so that the pressure reduced. The valve VSL between the first container B1 and the drive negative pressure fluid storage SAL is opened and from the fluid reservoir SAL working fluid flows into the first container B1, whereby there the pressure P1LC and the Fluid quantity M1LC sets. By overflow of Working fluid from the fluid reservoir SAL in the container B1, the pressure in the fluid reservoir SAL decreases.

advantageously, can in an intermediate step, not shown, between step B and step C, namely after closing the valve VSH and before opening the valve VSL, the container B1 deflated by briefly opening the valve VE, d. H. on pressure of the fluid source FQ, usually ambient pressure be brought, whereby the amount of fluid in the container B1 further reduced and in step C, in which the valve VE again is closed, a stronger negative pressure is generated.

Finally, in the transition from step C to step D, the valve VSL is closed, whereby the reduced pressure in the fluid reservoir SAL is maintained and the input valve VE is opened, so that working fluid flows from the fluid source FQ and in the first container B1 a pressure P1L and a Fluid quantity M1L sets what the situation 2 equivalent. The cyclic operation of the device then continues cyclically with a new step A.

A drive power or a part thereof can also be obtained by referring to the 2 and 3 a pressure gradient which temporarily develops during the change from one partial cycle to the next partial cycle counter to the direction of flow between two containers, which are pressure compensated during the residence time in the flow direction, is utilized as drive power. For example, at Change from the container position to 3 in the container position 2 an initially possibly still given pressure gradient from the still warm container B3 are exploited to the still cold container B2 via an additional line with a switchable valve to provide a drive power when overflow from the container B3 to B2 container in a fluid drive, which also, for example in the form of a spring, can be stored as mechanical energy. Due to the subsequent temperature equalization of the container B2 to the warm heat carrier WH and the container B3 to the cold heat carrier WL arises regardless of the described back flow again the same state at the end of the residence time as without such a return flow.

In yet another embodiment, the drive power for rotating the cylindrical body by means of a bimetallic arrangement, for which in 10 an example is sketched. A gear ZA rotationally fixedly connected to the common shaft WE of the cylindrical body is engaged with a dental arch of a gear ZB provided with a tooth structure over at least part of its circumference. Connected to this non-rotatably is a control disk ST, which has two stops A1 and A2 for a control pin SB. A working bimetallic strip AB is in thermal contact with a container BM or a heat medium surrounding the container or a working fluid or displacing fluid within the container. The bimetallic strip is shown in one of two end positions of the control disk ST and the gear rotatably connected thereto ZB. A free end of the bimetal strip AB is coupled to a rack ZS, which in turn is in engagement with a gear ZR, which is rotatable relative to the gear ZB with the control disc ST about the axis of rotation AZ and is coupled to the control disc via a coil spring SF. When a change in the temperature acting on the bi-metal strip AB temperature extends from the drawn curved shape in a less curved shape and this shifts the rack to the right and rotated under tensioning the coil spring SF the gear ZR relative to the control disc and the gear ZB , Control disk ST and gear ZB are held firmly by means of a control pin as long as the moment exerted by the spring on the control disk torque is smaller than the Losreißmoment of engaging under a contact force in a recess of the control disk control pin SB. If the Losreißmoment the spring-held control pin SB exceeded, the control pin moves out of the savings and relaxing the previously biased coil spring, the gear ZB is rotated and in turn rotates the gear ZA on the shaft WE.

Of the Control bolt can via a double lever assembly with levers SH1 and SH2 are driven via another bi-metal element SB be. About a set screw SS, the contact pressure a spring holding the bolt in a locked position FE be changed to the breakaway torque of the Precise adjustment of the control pin.

11 shows an arrangement in which a plurality of cylindrical bodies, each with two containers BA, BB with parallel roll axes laterally offset from each other around an interior HR are grouped and can occupy relative to this two different rotational positions. The plurality of cylindrical bodies WP are rotatable in synchronism about their respective axes of rotation and fitted in openings of a wall WW. The surfaces of the roll body WP can be sealed in the openings of the wall WW against this and thus seal an inner space HR against an outer space KR. By way of example, the interior HR may be at a higher temperature than the outside space KR surrounding the arrangement at a lower temperature by supplying a hot medium. In the 11 The viewer assigning side of the room HR can also be completed or preferably from the plane of the 11 be continued out. Openings of the containers BA, BB formed in the cylindrical body WP are advantageously on the viewer in 11 side away in a control chamber SR continued and there via suitable valve arrangements for the purpose of cascading the individual containers in one or more flow paths in one of the described or based on the 13 still explained way connected. The containers are advantageously synchronously rotatable about their respective central longitudinal axes and displaced from the outlined position in 180 ° rotated layers, after which the container BB facing the interior HR and the container BA are the outer space KR and through the respective heat transfer temperature changes of the working fluid in the containers are effected.

12 shows a device for the utilization of radiant energy, in particular solar radiation for obtaining mechanical power according to the described principle. The arrangement contains, within a side facing at least the radiation SO, a transparent housing within which a plurality of roller-shaped bodies WS with parallel, laterally spaced roller axes are arranged. The side of the cylindrical body facing the radiation SU is heated by the incident radiation SO. The radiation SO forms the heat source in this case. The heat sink is formed by a fluid which on the side facing away from the radiation SO side of the roll Migen body flows around them and which is supplied for example via an input terminal KE and discharged through an output terminal KA. The serving as a heat sink fluid may for example be water. In a housing VK at one axial end of the cylindrical body WS can advantageously be housed a valve assembly. A drive device can advantageously be arranged in a further housing GG at the axially opposite end of the roller body WS. By means of the drive means in the housing GG, the cylindrical bodies are synchronously rotated about their respective roll axes between two staggered positions of 180 °, the rotation advantageously being discontinuous in steps of 180 ° corresponding to two partial cycles of one cycle. The rotation can in turn be carried out alternately in opposite directions or in the same direction in one direction.

13 shows an advantageous coupling of the cylindrical body or formed in these in the already multiply described manner containers BSA, BSB. In the in 13 sketched position, the container BSA facing the radiation SO. The containers BSB of the cylindrical bodies WS are facing away from the radiation SO in contact with a cold heat carrier WL of a heat sink. The roller-shaped bodies can be sealed against one another via intermediate seals ZD and against a housing edge surface via edge seals RD in order to reliably separate the upper half space, via which the radiation SO is incident, from the lower half space with the cold heat carrier WL. To improve the seal, an overpressure or underpressure can be additionally generated in the first container via an opening DE at the edge seals.

The cylindrical bodies WS are continued in the example shown in the axial direction with flanges BF in the housing VK. Between the flanges h and the cylindrical containers, a fluid seal surrounding the shafts SW of the cylindrical bodies and / or a thermal insulation may be provided. The roller-shaped bodies have diametrically opposite openings OS in each of the two containers BSA, BSB and are surrounded in the region lying axially in the housing VK by guide tubes RF or circular-cylindrical recesses in a guide body. In these guide tubes connecting lines VL are connected at diametrically opposite positions, which form parts of the flow path for the working fluid in the containers BSA, BSB. The openings OS come in the sketched position and in a relation to this rotated by 180 ° position respectively with the connecting lines to cover so that depending on the pressure gradient working fluid can flow into a container or can flow out. If, at the end of a subcycle, the group of roller bodies WS is rotated synchronously about the respective roller axes of the roller bodies via the drive means housed in the housing GG, the openings OS are rotated against the connecting lines to be considered fixed and sealed against the inner walls of the guide tubes via sliding seals GD. In such intermediate positions during the rotation of the roll body WS, the containers BSA, BSB are closed and only when they reach the next, opposite to the position in 13 rotated by 180 ° end position, the flow paths between containers of laterally immediately adjacent roller bodies WS are open again. The connecting lines are arranged so that in each case the opening of one of the incident radiation SO facing container is connected via a connecting line with the opening of the radiation SO remote from the container of the adjacent roll body. Condensate separators KA can be inserted in the connecting lines. In the preferred use of air as the working fluid ambient air via a filter FI and a condensate KA via a connecting line VL can be supplied to the first cylindrical body and compressed air at the output of the last cylindrical body to be fed to a compressed air tank DB.

In another embodiment, the arrangement according to 12 and 13 Also be provided to exchange the heat source and heat sink and the connections KE, KA the 12 to flow a warm fluid and to give heat radiation into the environment, especially at night. Advantageously, one and the same arrangement during the day under solar radiation after 12 and 13 operated type described and the operation at night reversed.

In the 13 sketched arrangement and coupling of connecting lines and openings in walls of the container or with this twisted Auskopplungsstutzen is also applicable to other arrangements, in particular arrangements of the kind outlined in other examples, transferable. In this case, the openings OS which overlap in a position with the connecting lines form in the connection areas of the containers, which are sealed in other rotational positions against the wall of the guide tubes, the valve devices in the sense of the devices according to the invention. Separate measure taken to unidirectional controls unnecessary, since only by the temperature and pressure conditions, a stream of working fluid is always set in a flow direction.

The as pressure difference in the fluid reservoirs SAH, SAL stored energy can be supplied to a pneumatic drive, which causes or supports the rotation of the assembly about the axis of rotation DA. It can also be the drive 11 be connected only between each one of the fluid reservoir SAH, SAL and ambient pressure, in which case advantageously each of the fluid reservoir is used for each one of two rotations within a complete cycle. It can also be provided only one of the two fluid storage, SAH or SAL. Corresponding arrangements can also be provided for subsequent stages of the flow path.

The above and those specified in the claims and the features that can be seen in the illustrations are both individual and also advantageously feasible in various combinations. The invention is not limited to the described embodiments, but in the context of expert knowledge in many ways Way changeable.

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - US 6240729 B1 [0003]

Claims (36)

Device for obtaining mechanical energy from the temperature difference between a heat sink and one of these compared to warmer heat source using a working fluid having at least one flow path goes through with predetermined flow direction, in which at least one first fluid container and at least a downstream of this second fluid container and Valve means are arranged, which the working fluid volumes complete against the direction of flow and are openable in the flow direction, and by means Which cyclically alternating in a first subcycle the increase the pressure of the working fluid in the first fluid body by action the heat source and a reduction in the pressure of the working fluid in the second fluid container by the action of the heat sink and in another subcycle of the same cycle a reverse one Change the pressures cause, with a downstream the flow path occurring pressure gradient by opening the valve devices in the flow direction verminderbar is and a transport of working fluid in the specified flow direction causes. Device according to claim 1, characterized in that that an increase in pressure of the working fluid by heating a positive displacement fluid in the containers and a Pressure reduction of the working fluid by cooling the Verdrängerfluids takes place and Wärmeleiteinrichtungen between the displacer fluid and the heat source or the heat sink are present. Device according to claim 2, characterized in that that in at least one fluid container working fluid and Displacement fluid are identical. Device according to claim 2, characterized in that in at least one fluid container, the displacement fluid a variable partial volume of the container volume occupies and by a movable, especially flexible partition is separated from the working fluid. Device according to one of claims 2 to 4, characterized in that the heat conducting device at least partially formed by a container wall. Device according to one of claims 1 to 5, characterized in that by means of drive means the Fluid container relative to heat source and heat sink are movable. Device according to claim 6, characterized in that in that the fluid containers are arranged to be rotatable about an axis of rotation are. Device according to claim 7, characterized in that that the fluid container between two rotational end positions are rotatable in opposite directions. Device according to claim 8, characterized in that that the Drehendstellungen by at least 120 °, preferably at least 150 ° offset from each other about the axis of rotation are arranged. Device according to claim 8, characterized in that that the fluid container cyclically continuously in one direction of rotation are rotatable about the rotation axis. Device according to one of claims 6 to 10, characterized in that the plurality of fluid containers are coupled together in their movement. Device according to one of claims 6 to 11, characterized in that at least part of a drive power for the drive device from the temperature difference derived between heat source and heat sink is. Device according to one of claims 6 to 12, characterized in that the drive means a Bimetallic element included. Device according to one of claims 1 to 13, characterized in that the sub-cycles each one temporally shorter movement section and one temporally longer dwell section included. Device according to one of claims 6 to 14, characterized in that the valve means at least a check valve included. Device according to one of claims 1 to 15, characterized in that the valve means at least contain a controllable valve. Device according to one of claims 1 to 16, characterized in that the valve means at least at the end of a partial cycle for pressure gradient in the direction of flow of the flow path are open. Device according to claim 17, characterized in that that the valve means during the vast majority Duration of a partial cycle for pressure gradient in Flow direction are open. Device according to one of claims 1 to 18, characterized in that arranged between a first fluid container in the flow direction and in a last fluid container, at least one intermediate fluid container in the flow path is. Device according to claim 19, characterized in that that at the end of a subcycle after a degradation of a pressure gradient between an intermediate fluid container and an immediate downstream in the flow direction Fluid container the degradation of the pressure gradient closed in the direction of flow valve device and another valve device to the other, open upstream fluid container becomes. Device according to claim 20, characterized in that that a fluid flow through the further valve means for recovery used by drive power for the drive device becomes. Device according to one of claims 1 to 21, characterized in that the container parts at least a roller body about the axis of rotation. Device according to claim 22, characterized in that that at least two containers in a roll body are integrated and occupy separate angular ranges around the axis of rotation. Device according to claim 22 or 23, characterized that a plurality of roller bodies in the direction of the axis of rotation behind one another are arranged. Device according to claim 24, characterized in that that container of the plurality of roll body over Fluid lines and valve means are fluidly connected. Device according to one of claims 23 to 25, characterized in that on the side of the heat sink and / or the heat source a curved around the axis of rotation, from the at least one roller body spaced wall limited to a surrounding space. Device according to one of claims 23 to 26, characterized in that at least a part of the valve means with fluid lines in the at least one roller body is integrated. Device according to one of claims 23 to 27, characterized in that at least a part of the valve means is integrated with fluid lines in a hollow shaft. Device according to one of claims 23 to 28, characterized in that at least a part of the valve means offset axially against the at least one roller body is arranged. Device according to one of claims 1 to 29, characterized in that at least a part of the valve means arranged heat insulated against the heat source is. Device according to one of claims 1 to 30, characterized in that the heat source and / or Heat sink a gaseous or liquid Medium contained as a heat transfer medium. Device according to claim 31, characterized in that that the heat source is a gaseous medium and the heat sink a liquid medium as a heat transfer medium contain. Device according to one of claims 1 to 32, characterized in that the heat source a Radiation absorber contains. Device according to one of claims 1 to 33, characterized in that the working fluid is a gas, in particular Air is. Device according to claim 34, characterized in that that the gas is downstream of the last fluid container the flow path a compressed gas storage tank is forwarded. Process for obtaining mechanical energy the temperature difference between a heat sink and a this opposite warmer heat source using a working fluid having at least one flow path goes through with predetermined flow direction, in which at least one first fluid container and at least a downstream of this second fluid container and Valve means are arranged, which the working fluid volumes complete against the direction of flow and can be opened in the flow direction, where cyclic alternately in a first subcycle, the pressure of the working fluid in the first fluid body by the action of the heat sink increased and the pressure of the working fluid in the second fluid container decreases and the pressures in another subcycle the same cycle are reversed, with a occurring downstream of the flow path pressure gradient by opening the valve devices in the flow direction is reduced while transporting working fluid in the flow direction becomes.