HUE033411T2 - Eljárás alacsony hõmérsékletû termikus energiának mechanikai energia segítségével történõ magasabb hõmérsékletû termikus energiává történõ átalakítására, és viszont - Google Patents

Description

METHOD FOR CONVERTXHC3 THERMAL EHERGY RT h LOW TEMPERATURE IRTÓ THERMAL EMEEGI AT A RELATIVELY HIGH TEMPERATURE BT MEERS OF ME-

CHARICAL ERERGI, AMD PICE VERSA

Description

The invention relates to a method for converting thermal energy at a loo temperature lute thermal temperature at a relatively high temperature by means of mechanical energy ana vice versa, i >e,, converting thermal energy of a relatively high temperature into thermal energy of a relatively loo temperature Muring the release of mechanical energy, with a norRing medium that rune through a closed thermodynamic circulation process, wherein the circulation process exhibits the following working steps ;

Reversible adiabatic compression of the working medium, Isobaric conduct ion of heat away f rom the working medium. Reversible adiabatic expansion of the working medium, Isobaric supply of heat to the working medium, wherein, in order to increase or decrease the pressure of the working medium during compression or expansion, respectively, the working medium is relayed essentially radially outward or inward in relation to a rotational axis, generating an increase or decrease in the centrifugal, force acting on the working medium Λ

In addition, the invention relates to a device for implementing a method according to the invention with a compressor, a expansion unit and a respective heat exchanger for the supply or removal of heat, wherein the compressor and expansion unit are mounted so that they can rotate around a rotational axis, and tte and/or expansion unit are designed in mch a way ^ thafc the working medium in the compressor is esnentxaiiy oarrred rMially outward in mimim to « rotational tialXv carried radially inward in the expansion wnit;, cnerecy inoroasinf or decreasing tim pressure by increasing « dacreaa-inS the centrifugal force acting on the working medium, known from prior art are various devices, so-called bead pumps, in which a motor is normally used to heat a working medrum at a low temperature to a relatively high temperature W imzmmmg the pressure, In known heat pumps, the working medium runs through a thermodynamic circulation process, wherein this thermodynamic circulation process encompassae evaporation, compression:, liguetaction, and expanding the: working medium at an inductor; i,e., the aggregate condition of the working medium normally changes*

In known heat pumps, use is normar iy made oi the coolant R..vi4a or a mixture comprised of R134a among other ingredients, which does not have a deleterious effect on the crone, hut still has a 1300 times greater of a. freenhoUse-genefstihf effect than the same quantity of C02, Such methods are esceufciaiXy implemented according to the Carnot process, and exhibit a theoretical performance number or COP (coeff icient: of performance) , i .e, .. a correlation between the released heat to the used electrical en·· erfy of approx, 5 - 5 (when -pumping” the working medium from 0 to 35°C) . However, the best performance coefflelenc achieved to date only came to 4,9; m a rule, good hast pumps currently produce a performance coefficient of approx, 4.7, known from DE 27 23 134 hi: is a device with a hollow rotor. wherein g ti ide pas wages or gui^e vanes are here provided on the opter periphery ef the rotating: foody, m that a high relative: velocity arieea between ehe guiae passages and working medi-urn, such guide vanes al^o produCe very high losses in flow energy, whsch leads to a reiativelv low performance coefficient. m 30 18 Id® Ä1 disolocnn^ 03^r to provide a theroodynaole circulâti°n prooee# aa ideal as possifela , a'· work ing modxnm to a atteng c a n t r i fuga X force field. The method shown is hasad, on a Carnot, circmlation process . An expansion of the gas 1$ caused by flowing the gan against the direction of the cent til agai tor ce ; j.n a.u analogonn manner, the gas is com -pressed when flowing in the direction of the centrifugal force. Heat supply and/or removal are accomplished; by beat exchangere* bh 22 id rn$ Ä1 describes another thermodynamic method imin# centrifogal force, A rotor rotatable ar s u m s shaft ha s a oow; preaeion duct and an expansion duct: as well ass a connecting duct, wherein compression or expansion, respectively, of a gaseous working medium is caused by centrifugal effects. ttc ç8_> „>3B ä describes a method known as the ^Aobbucjt met.boo Äich is baaed on an openly designed thermodynamic process. A further compressor is known £ rom the article “Modified Roebuck compression device for cryogenic réfrigérâtion system: of super -conducting rotating machine" by jeong et aï.< using the centrifugal effect on a rotating gas for compression and/or expansion of a gas.

Known from WO 1998/30846 Al is a device that can be used as a re 1'rig arator or ä motor, whcrhih air is here used; as she working medium, aspirated from th# environment art! again iwdoased to t$m environment after being compressed or expanded. In such an open system, it; is dlsadvantAgamhs that: an angular momentum builds Up a« the work ing medium enters into the machine, and i s ret tered at the working medium exits the machine, thereby yielding significant friction losses<

Known from FR 2 749 070 hi is merely another type of heat pump with a conventional turbocompressor or a toothed displacer.

Further known, from GB .1, 217 BB2 A is a thermodynamic device that essentially does make nee of centrifugal force, hut is here also provided with ah induetick point ,;: thereby giving ride tü considerable friction losses,

On the other hand, numerous methods are also toe from prior art., which involve in particular converting the heat from geo-therínál liquid and geothermal vapor into electrical energy:. In the so-called KALIFA process, heat is released from water to an ammonia-water mixture, thereby already producing vapor at significantly lower temperatuies, which is used to power turbines. Buch a KALIFA process is described in OS 4: 4SS 563, for example.

While the attainment of very high performance coefficients is theoretiddily peealble in. ":fche most varied heat exchange methods/: conventional semrpressors and expansion units in which the working medium is compressed and expanded in the gageons raxigc usually have a relatively poor efficiency.

As a consequence, the obseci of the present invent .ion is to im- prove the efficiency or performance coefficient during the corn-version of thermal energy of. a loo temperature into thermal energy of a relatively high temperature by means of mechanical energy and vice versa,

This ia achieved according to the invention by routing both the working medium during the cloned circulation process as well as the heat exchange media for heat supply and removal around the rotational axis, so that the flow energy of the working medium is- essentially preserved during the closed circulation process, A clearly higher efficiency is achieved by the utilisation of centrifugal acceleration and retention of flow energy in the working medium toy comparison to conventional compressors, in which the high velocity of the working medium at the periphery of the compressor is converted into pressure., theretoy yielding a poor efficiency » In like manner, the efficiency- £0- increased during expansion by reducing the pressure of the working medium, in the course of: expansion hy decreasing the centrifugal force. This significantly improves the performance coefficient or efficiency of the entire method,

In addition, it is advantageous for improving efficiency that the working medium be gaseous over the entire circulation process, since work can he recovered in a way that makes sense from the standpoint of energy as the gaseous working medium expands. While not being relevant in terms of energy with respect to liquid media, further, the influence: on efficiency in the gaseous range is greater than in the 1-phase range.

With regard to a high, compression by means of centrifugal acceleration, it is advantageous to use gases with a lower specific thermal capacity at a constant pressure (op) or with a higher

v— fVl V ^hsity. As a consequence, the working medium used it pzeZe**x‘ "" t noble gas; in particular krypton, xenon, argon or radon,, oi " fixture thereof . Further, it has been demonstrated; he Ä bni^:a hi«, for the nressure in the closed circulation process to :‘ oh at laast: in excess of BO bar, in particular in excess o*· bar, preferably essentially 100 bar, i.e,,. for the pressure comparatively high during the entire process. The compar®" lively high pressure makes it possible to keep the pressure in the heat exchanger low, since the transfer of heat M 00^9^ -ably high at cottarstiveIf low flow rates.

Jurying out the circulation process in close proximity to hUfe yr:it:ica.l point of the gaseous working medium further improve-the overall efficiency or Increases the performance coe££ie-i eat' ' ^herein the critical point is present as a fund tien of the u£:C^ horyi^g medium at * varying pressure: Of temperature , the performance coefficient or overall, effieiercy is maximised harixig expansion take place in an entropy range as close as Ρα(χ: sible to the entropy of the respect ive: critical point, Further, it is advantageous for the lower expansion temperature to H® just over the critical point. The critical point can be adjusted to the desired process; temperature using gas mixtures. Ä structurally Simpie and eifieient cooling or heating of the "WdÂinf can be achieved by removing and supplying heat using a. heat exchange medium with an isentropic exponent Kappa -1, i . e. , media in which the temperature remains essentially constant given a pressure increase, in particular a liquid heat exchange medium.

In the device for implementing; the method according to the invention,. the heat exchangers are designed to rotate together with the compressor and expansion unit/ in which the working medium is relayed around the rotational axis during: the closed circulation process/ so that the flow energy of the working medium is essentially retained during the closed circulation process/ As already deserihed; shore in conjunction with the method according to the indention/ this yields a distinct improvement in efficiency during compression and expansion of the working medium/ thereby clearly improving the performance coefficient or efficiency of the device according to the invention by comparison to known devices,

In terms of a structurally simple configuration of the heat exchanger, it is advantageous for the heat exohangers to each exhibit at least one pipe that carries a liquid heat transfer me ·· diimu

Mith respect to achieving a low'-flbetion transition from the compressor to the expansion unit/ 1/0,., to retain the flow energy of the working medium, it is advantageous that the expansion unit connect directly to the compressor by way of the heat exchanger, In terms of a structurally simple configuration of the device/ it is advantageous to mount the impellers of the compressor and expansion unit on a shared torque shaft.

One structurally easy way to increase the pressure of the working medium via centrifugal acceleration is to provide a casing that rotates together with the impellers of the compressor and expansion out,

In order to achieve an efficient cooling of the compressed working medium, it is advantageous that the casing accommodate a coro taring heat exchanger. The co-rotating heat exchanger is most advantageously arranged on the outside: periphery..

However, Instead of the casing co~ rotating· with the impellers, it is just as conceivable that the impellers be enveloped by a fixed casing. This enables a reduction in the structural outlay. In order to avoid friction losses of the working medium: on a pipe of the heat exohanger connected with the fixed erasing, however, it is advantageous for the pipe of the heat exchanger to be partially incorporated into the casing, wherein, the surface of the fired casing that domes into contact with the working; medium has the smoothest possible design.

In order to avoid outer, rotating parts,. it makes sense to provide a torsion-'resistant casing that envelops the compresser and expansi on uni t,

To achieve an efficient supply of heat to the working medium, it is advantageous for the two heat exchangers to be incorporated in the casing.

Providing at least one rotatably mounted pipeline system that circulates the working medium yields a devise with a comparably low overall weight, since the wall thickness of the pipes; carrying the working medium can be reduced by comparison to that of the casings accommodating the working medium,

With respect to compressing the working medium in the pipeline system via centrifugal force, it is advantageous for the pipeline system to exhibit linear compression pipes running in a radial direction.

In order to reliably circulate the workixig medium in the pipeline ays tern, .it is advantageous for the pipeline system to exhibit expansion pipes bent against the rotational direction of the torque shalt., The expansion pipes can here have a. circularly bent cross section to simplify the structural design. As an alternative, the expansion pipes can also exhibit a bend with a cross sectional radius that constantly diminishes tosard the instant center. This makes it possible to reduce any turbulence that arises in the pipeline system.

In addition, a floe of the sorbing medium in the pipeline system is reliably ensured by incorporating a bucket wheel in the pipeline eye tern that rotates relative to the pipeline system. The bucket wheel is designed as a compressor: expansion turbine or guide vane, and can here be arranged in a toreion-resistant manner, wherein the torsion-resistant arrangement gives rise to a relative movement to the rotating pipeline system. It is also conceivable that the buchet wheel, for example, be provided with a motor for generating or nsing a relative movement to the pipeline system, or a generator, which converts the generated shaft output into electrical energy via the relative movement of the bucket wheel,

With regard to a simple and efficient heat supply or removal, it is advantageous for axially running sections of the pipeline system to be enveloped by coaxially arranged pipes of the heat exchanger,

In order to supply the difference between the necessary energy from compression and recovered energy from expansion to the device during operátich as a heat pump, it is advantageous that a motor be connected with the torque shaft of pipeline system.

To convert che mechanical energy obtained from varying tempera--ture levels into electrical energy, i.e. , when using the device an a thermal engine, it is advantageous for a generator to be connected with the torque shaft,

The invention will be described in even greater detail below based on preferred exemplary embodiments depicted in the drawings, but not be limited thereto. Of course, combinations of the described exemplary embodiments are also possible . Specifically shown in the drawings arc ;

Fig, 1 a diagrammatic process block diagram of the device according to the invention or the method according to the invention during operation as a heat pump;

Fig. a a sectional view of a device according to the invention with a co'-rotating easing;

Fig. 3 a sectional view of a device according to the invention with a fixed casing?

Fig. 4 a sectional View similar to Fig, 3, but with a motor incorporated inside;

Fig, 3 a sectional view of another exemplary embodiment with pipelines that carry the working medium;

Fig. 6 a section according to the VI-VI line in Fig. 3;

Flo.. ? a. 3action according to the VII-VII lino in Fig. I;

Fig. 8 a sectional view of another exemplary embodiment with a. pipeline evetem that accommodates the working medium;

Fig. 3 a perspective view of the device according to Fig. 3 ;

Fig. 1.0 a sectional view of a device similar to Fig. S, hut with the turbine motionless? and

Fig. IX a sectional view similar to Fig. 10, but with a turbine rotating relative to the pipeline system.

Fig. 1 provides a schematic view Of a process block diagram of a thermodynamic circalation process of the kind basically known from prior art. In the application as a heat pump depicted, a compressor 1 is initially used to isentropieallv compress the gaseous working medium, Xsonaric beat removal takes place subsequently by way of a heat exchanger 2, so that thermal energy with a high temperature is released and circulated (with water, w&amp;ter/antifreese or some other liquid heat transfer media) to a thermal circulation system.

An isentropio expansion is then performed in an expansion unit 1 accommodated in a turbine, thereby recovering mechanical energy. Another heat exchanger 4 is then used to effect an isobaric heat supply, thereby supplying thermal energy at a low temperature to the system fey way of a circulation system (with water, water/ant if rente , brine or some other liquid heat transfer media) . In this case, thermal energy is normally extracted from well water, from so-called depth probes, in which heat is extracted from the: heat exchangers si.tna.teci at a depth of up to 2DO m in the earth and supplied to the heat pump, or the thermal energy is extracted from large heat exchangers (pipelines) lying just underground or from the air. The isobar!c heat supply is again followed by isencropic compression by means of compressor :i, as described above .

In cases where the device according to the invention or method according to the invention is used to convert thermal energy at a relatively nigh temperature into thermal energy at a low temperature, the aforementioned circulation process takes place in the reverse sequence. During operation as a heat pump , a motor 5 is provided for powering a torque shaft 5'; during operation as a heat engine, the motor is replaced by a generator 1 or motor generator 5.

Fig, 2 shows a device according to the invention in which the motor 5 uses a torque shaft 5" to power a compressor 1 with a eo-rotating casing: s, m addition., the impellers 1- of the compressor 1 are powered by the torque shaft S' driven by the electric motor S.. so that the noble gas accommodated in the sealed, motionless easing 8, preferably krypton or xenon, is compressed in the cg-rotating casing 6 via centrifugal acceleration.

The co-rotating casing 6- incorporates a spiral pipeline 9 of the heat exchanger 2, which holds a heat exchange medium, e. g,, water, The comparât iveiy cold water is incorporated via an inlet 10 into the spiral pipeline S in flow direction 10 U and is arranged on the outside periphery inside the co-~rofating casing so as to achieve an isobarxc removal of heat from the working medium with the working medium at the highest possible pressuré, making it possible to discharge comparatively warm water at the ΟΧ5ΛνΧ&amp;· λ»· Λ· X s'

The working· medium thon, flows without any significant loss in flow to impellers 3' of the expansion unit 3« from which mechanical energy is recovered. An isobaric supply of heat then, takes place in the motionless casing 8 via a spiral pipeline 12 of the other heat exchanger 4, until the working medium is again subjected to adiabatic isentropio compression via the impellers 31 of the compressor 1,

However, it is only important that the energy of the working medium held in the device compris ing a sealed system, retain its flow energy during compression in the compressor 1 and/or expan -Sion in the expansion unit 3,. and a pressure increase or decrease of the working medium is attained solely via centrifugal acceleration of the gas molecules of the working medium. As a result,, the efficiency or performance coefficient can be significantly improved while converting thermal energy at a low temperature into thermal energy cf a relatively high fcery>erature via electrical or mechanical energy and vice versa.

Fig, 3 shows another exemplary embodiment, wherein a motionless interior casing 01 is hare provided. This simplifies the structural design. To keep down flow losses of the gaseous working medium or retain as much as possible Of the angular momentum for the working medium, the motionless surfaces which the working medium contacts are as smooth as possible, and there are no heat transfer pipes lying transverse to the flow, which would further increase the pressure loss. The spiral pipeline 3 of the heat exchanger· 2 is not freestanding, but rather incorporated in the motionless casing €' with a smooth surface 21 < in order to increase the performance coefficient or efficiency of the overall dévie®, insulation mat@ri.al 13 is incorporated inaidé the motion! es a casing S',

Fig. 4 snows another exemplary embodiment; which essentially corresponds to that on Fig. 3, the only oil carence being the ar rangement of the motor 5; specifically, the motor 5 in this exemplary embodiment is accommodated inside the fixed casing 6.

Lines 14 that run through statically compression-proof bushings IS as well as a stationary motor shaft 16 are provided to supply the motor S with power, the motor S is here connected with the compressor 1 or expansion unit 3, so that these eo~rotate. This advantageously eliminates dynamxc gaskets {gas and liquid gaskets} f thereby reducing maintenance work,

Fig, 6 to 7 show another exemplary embodiment of the device according to the invention, wherein all parts exposed to the pressure of the working medium are designed as pipes or a pipeline system 17, therePy reducing' the overall weight of the device, and: allowing a thinner wall thickness for the pipes 17 by comparison to that of the casings 6, 6' and 6 depicted on Fig, 2 to 4 ,

The working medium is here initially compressed in the radially running compression pipes IS of the pipeline system 17 of the compressor unit X owing to centrifugal acceleration. The heat exchanger 2 here exhibits pipes IF that are arranged coaxially relative to the outlying section of the pipes 17 running in ah axial direction, and envelop the respective pipe 17, so that the heat of the compressed working medium is released count.® rear -rently to the liquid heat exchange medium of the heat exchanger "V >

The working modi urn is subsequently expanded in expansion pipes 20 :o£ the expansion unit 3}. The expansion pipes 20 are here bent opposite the rotational direction 21 of the device, wherein a circulation of the working medium reliably arises as the result of the backward pipe bend (compare Fig, 7} <

As evident in particular on Fig, 7.. the expansion pipes 2 0 can be bent in a semicircular manner, making the latter easy to manufacture in terms of structural design. The working medium cub·· seqnently flows in an axial direction in the pipeline system 17, wherein the low-pressure heat exchanger S here again exhibits a coaxially arranged pipe 17, so that heat from the liquid heat exchanger medium .is: released to the cold expanded working medium.

As evident in particular on Fig. 7, this yields 2 closed pipeline systems 17 essentially shaped like the figure eight when viewed from above for the working- medium, which are offset by SO* relative to each other. Of course, the pipeline system 17 can also exhibit a larger number of lines 20 ; only the rotational symmetry of the arrangement must be preserved for purposes of easier ha lane i ng,,

The pipes 19 of the heat exchangers 2 and 4 arranged coaxially relative to the axially running sections of the pipes 17 are interconnected by lines 221 23, 24, 25 that carry liquid, wherein this pipeline system 22 to 25 is rigidly secured with the re -ma in ing device, so that the: lines 22 to 25 co- rotate. The: 11. quid heat transfer medium is supplied to the pipeline system 17 via a feed 26: of a static distributor 25; the heat exchange medium is then relayed via a co-rotating distributor 27 through the line 22 to tne heat exchanger 2, in which it is heated and returned through line 2 3 to the to •'-rotating distributor 27, The heated heat transfer medium is then relayed tes the heater circulation system by way of the static distributor 20 or a discharge 26',

The cold heat exchange medium of the heat exchanger i is guided vis a feed 28* of a static distributor 26.. conveyed with another co-rotating distributor 27 in this co-rotating line 25 to the loo-ore estire heat exchanger 4., where heat is released to the gaseous working medium. The heat exchange medium is then routed via the co-róhating line 25 to the co-rotating distributor 25 and then the static distributor 28, after which it exits the device by way of a discharge 28r ' , Ä motor 5 is again provided. to power the compressor 1.. heat exchanger 2, 4 and expansion unit 3.

Fig, B and 9 show an exemplary embodiment similar to the one on Fig, 5 to 2, hut the expansion pipes 20 are here not semicircular in terms of cross sectional design, but rather exhibit a. continuously diminishing radius toward the midpoint of the rotational axis 30, This yields a. monotonously dropping, delayed movement of the working medium, making it possible to reduce any arising turbulence. In addition, the exemplary embodiment shown on Fig, 8 and 5 depicts two independent pipeline systems 17 offset by go-3 relative to each other, 'wherein three compressions, expansions, etc. take place per pipeline system 17.

Fig 10 shows another exemplary embodiment, which in large part corresponds to the one on Fig, S to 7, except that the circulation of the working medium is not achieved by means of pipes 20 bent opposite the rotational direction, but rather with a wheel 31, which acts as a compressor or turbine. The wheel 31 is fixed in place, wherein the relative rotational movement to the pipes 17 sur reverting the wheel 31 produce a flow of the working medium in the pipes 17.

In this ease, the working medium is expanded in the pipee 17 of the expansion unit 3 and routed to the wheel 31, wherein the wheel 31 is accommodated in a wheel casing 32: which is closed by means oi a cover 33. The wheel 31 is mounted so that it can rotate via bearings 34, nut does exhibit permanent magnets 33, which interact with permanent magnets 33 arranged in a torsion-resistant manner outside the wheel casing 32, thereby fixing the wheel 31 in place. The magnets 36 here rest on a static shaft 37,

Fig. 11 shows a device designed very similarly to the exemplary embodiment depicted in Fig, 10, but the relative rotational movement of the wheel 31 to the pipes 17 of the Compressor and expansion unit 1 and 3 is here generated by means of a motor 38, The motor 38 is secured with the co-rotating distributor 2? in a torsion-resistant manner, The power is here supplied via lines 33, which are accommodated in a shaft 40. The shaft 40 exhibits contacts 41 for purposes of power transmission. In this embodiment, the power supplied by the motor 5 is intended only to overcome the air resistance of the rotating system,

As a result, the latter can therefore be omitted by using turbines in the circulation system of the liquid heat transfer me· drum, which remove thie power from the circulation. The power required for overcoming the air resistance is then additionally provided by the pumps, which drive the circulating liquid heat transfer medium..

Claims (5)

1. Itpbadalnüli isénypcntök

   1. SiJÉráa alacsony hőmérsékletű termikus energiának mechanikai energia segítségévet történő magasabb hőmérsékletű termikus energiává történő: italakítiaira, is vissent:* olyan munkakö2eggei., amely zárt tertnodinamikii kőrföfpmatöi: megy át, amelynél a körfolyamat a kivetkező lépéseket tartalmazza; - a rnunkaközeg adiabatikus kompfiméiása, ~ a munkáközegböl izobár höeivézetés Meseritl közeg segítségévei, - a munkaközeg adiabatikus expandiiiatása, ~ a munkaközéghez liebár hlbevezetés hőcserélő közeg segítségévet, amelynél a munkaközeg komprimátás.. ilietve expandáltatás alatti nyoniésnöveíéséhez, síiéivé -csökkentéséhez a niunkaközeget egy forgástengelyhez képest lényegében sugánmnybah kifelé, illetve befelé vezetjük, szilát a munkaközegre ható centrifugális erő növekedését, illetve csökkéhislf hozzuk létre, azzal Jellemezve, bogy a munkaközeget m zárt körfolyamat alatt, valamint a hőcserélő közegeket a bö hszzávezetéshez és elvszefésbéz a forgástengely körül úgy vezetjük, hogy a munkakozeg áramlási energiáját a zárt körfolyamat alatt lényegében féhhtaisulé
2. 2. Az fuigénfpont szerinti el|érá$; azzal jellemezve,, begy a munkaközeg, amely előnyösen nemesgáz, különösen kripton, xenon, argon, radon, illetve ezek keveréke, a teljes körfolyamat alatt gáz halmazállapotú.
3. 3. Az 1, vagy 2. igénypont szerinti eljárás, azzal Jellemezve^ bogy a nyomás a zárt körfolyamatban legalább 50 bar feletti, különösen 70 bar feletti, előnyösen lényegében 11© bar, 4. A 2, vagy 3. Igénypont szerinti eljárás, azzal Jellemezve* hogy a kárfolyamaiét a gáz halmazáiJspotu rntmkakőzeg kritikus pbhlflnak közeiében végitaék.. 5* A4 1 “4, igénypontek feármeivAe szerfátt epráé, azzal jellemezve, hogy a hé· elvezetéséhez és a hő hezzáyezétéséhaz kappe *1 izení rőpikus sxponensi hőcserélő kileget, kölinösen folyékony hőcserélő közeget aikalmaiuéis 6. ierendezês m 1~5. igénypontok bármelyike szerinti eljárás foganatosítására kompmsszoíraMli expanőiítaió egységgel (Ír és a Wö hözzávezetésáez, illetve a hé elvezetéshez megfelelő hőcserélővé! (2, % ahol a kompresszor (!) és az expandÉltatő egység (3) egy forgástengely körű! ferpfeetéah van esspágyazva, is a kompresszor (1). illetve az expândâltatô egység (3) úgy van kialakítva, hogy a murtkaközeg a kompresszorban 0) a forgástengelyhez képest lényegéhen sugárirányhan kifelé, illetve az ekpanpáliató egységben (3) lényegében sugárirányban befelé váh vezetve úgy, hogy m munkaközegre ható centrifugális erő növelésével, lelve csökkentésével nyomásnövekedést léivé csökkenést hozunk leire, azzal jellemezve, hogy a hőcserélők (2, 4) a kompresszorra! ffj és az expandálialé egységgel (Ij* amelyékbéh a munka közeg a zárt körfolyamat alatt a forgástengely kőről van vezetve, együttforgőih: úgy vannak kialakítva, hogy a rnynkaközeg áramlási energiája á Zárt körfolyamat alatt lényegében megmarad, 7. A 6. igénypont szériái berendezés, azzal jellemezve* hogy a hőcserélők p:( 4) mindegyike fátfelmaz legalább egy csövet {%· amelyen feiyékony hőcserélő közeg á ramlik ál 8. A 6. vagy A igénypont szét int; berendezés* azzal jellemezbe* hogy az expandáltatő egység; |3) a höcserélőkte: p*. 4) kemsztií kőzvefénöí a kompresszorhoz (i): osiiiakozlk.
4. 9, A i'-i- iiényponfok bármelyike szerint! beriendezéé* mzsê jeitéfffazv«*· teil a kompresszor és az expandáltak) egység (1 3} járókerekei (r, 3'} közös forgásíengeíyen (5‘) vannak csapágyazva, amelynél a kompresszor (1\ 3f és az expandáláfo egység (3 ) jérő kerekeivel (Γ) együttforgö ház: (6) van.
5. 10. Az 3-9, Igénypontok bármelyike szerinti berendezés, azzal jellemezve, hogy a kompresszort (13 és az expandáltatő egységet (3) körülvevő, forgás ellén rögzítettén elrendezeti: háza (8) van, amely a kit hőcserélőt H . Az i-?. igénypontok ibáimielylke szerinti berendezés, azzal jeiiemezve, hogy legalább egy, a rnunkaközeget a körben vezető, forgaliaféan csapágyazott csővezeték rendszere (3?) yai, aboi a csővezeték renészer (1?) iineánsan sugárirányban közödé komprimáló csöveket (10) éslvagy a forgástengely p!) forgásirányával ellentétesen hajlított expanöittalő csöveket (20) tartalmaz, 12. A 11. Igénypont szerinti berendezés, azzirt jellemezve, hogy az expandáítafo csövek (20) keresztmetszetben körív alakban vannak hafistvá, ahol az expandáltató csövek (tö) keresztmetszetben a forgási középpont (30) féíi iilándéan csökkenő sugáré hajíítást tartalmaznak. 13. A 11. igénypont szerinti berendezés, azzal jellemezve, hogy a csővezeték rendszerben (17) a csővezeték rendszerhez (17} képest forgó lapitkerik (31) van elrendezve. 14. A 13. Igénypont szerinti berendezés, azzal jellemezve, bogy a íapitkerék (31) forgás eilen rögzitetten van elrendezve. 13, A :0-14,. igénypontok bármelyike szerinti berendezés, azzal jellemezve, hogy a forgástengelyhez (5% illetve a csővezeték rendszerhez (17) villamos motor vagy generátor (5) van csatlakoztatva.