EP2183529B1 - Verfahren zum umwandeln thermischer energie niedriger temperatur in thermische energie höherer temperatur mittels mechanischer energie und umgekehrt - Google Patents

Verfahren zum umwandeln thermischer energie niedriger temperatur in thermische energie höherer temperatur mittels mechanischer energie und umgekehrt Download PDF

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Publication number
EP2183529B1
EP2183529B1 EP08782795.2A EP08782795A EP2183529B1 EP 2183529 B1 EP2183529 B1 EP 2183529B1 EP 08782795 A EP08782795 A EP 08782795A EP 2183529 B1 EP2183529 B1 EP 2183529B1
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EP
European Patent Office
Prior art keywords
working medium
heat
compressor
relaxation
circulation process
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EP08782795.2A
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German (de)
English (en)
French (fr)
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EP2183529A1 (de
Inventor
Bernhard Adler
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Ecop Technologies GmbH
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Ecop Technologies GmbH
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Priority to PL08782795T priority Critical patent/PL2183529T3/pl
Publication of EP2183529A1 publication Critical patent/EP2183529A1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B3/00—Self-contained rotary compression machines, i.e. with compressor, condenser and evaporator rotating as a single unit

Definitions

  • the invention relates to a device for carrying out a method according to the invention with a compressor, a relaxation unit and in each case a heat exchanger for heat supply or heat dissipation, wherein the compressor and the expansion unit are rotatably mounted about an axis of rotation and the compressor or the expansion unit are configured such in that the working medium in the compressor is guided essentially radially outwardly with respect to the axis of rotation or substantially radially inward in the expansion unit, so that an increase or decrease in pressure is produced by increasing or decreasing the centrifugal force acting on the working medium ,
  • thermodynamic cycle vaporizing, compressing, liquefying and expanding at a throttle of the working medium comprises; ie usually the physical state of the working medium changes.
  • the refrigerant R134a or a mixture consisting inter alia of R134a is used, which, although having no ozon destroying effect, however, has a 1300 times higher greenhouse-forming effect than the same amount of CO 2 .
  • Such processes which are carried out essentially according to the Carnot process, have a theoretical coefficient of performance or COP (Coefficient of Performance), ie a ratio of the heat given off to the electrical energy used of approximately 5.5 (when "pumping" the working medium from 0 to 35 ° C). In practice, however, at best a performance factor of 4.9 has been achieved; As a rule, today's good heat pumps achieve a coefficient of performance of approx. 4.7.
  • thermodynamic cycle as ideal as possible to expose a gaseous working fluid to a strong centrifugal force field.
  • the method shown is based on a Carnot cycle. Expansion of the gas is effected by passing the gas against the direction of centrifugal force; in an analogous manner, the gas is compressed as the gas flows in the direction of the centrifugal force.
  • thermodynamic method which makes use of the centrifugal force.
  • a runner rotatable about a shaft has a compression channel or an expansion channel and a connecting channel, wherein a compression or expansion of a gaseous working medium is effected via the centrifugal action.
  • thermodynamic device which basically makes use of the centrifugal force, but here also a throttle point is provided, so that considerable friction losses occur.
  • the object of the present invention is to improve the efficiency or the coefficient of performance in the conversion of low-temperature thermal energy into higher-temperature thermal energy by means of mechanical energy and vice versa.
  • a noble gas in particular krypton, xenon, argon, or radon or a mixture thereof is preferably used as the working medium.
  • the pressure in the closed cycle is at least 50 bar, in particular more than 70 bar, preferably substantially 100 bar, ie the pressure during the entire process is comparatively high. Due to the comparatively high pressure, the pressure loss in the heat exchanger can be kept low because the heat transfer at comparatively low flow rates is relatively high.
  • the critical point is present at different pressure or temperature, depending on the working medium used.
  • the total power efficiency is maximized by performing the relaxation in an entropy range which is as close as possible to the entropy of the respective critical point.
  • the lower relaxation temperature is just above the critical point.
  • the critical point can be adjusted by gas mixtures to the desired process temperature.
  • the heat exchangers with the compressor and the expansion unit, in which the working medium is passed around the axis of rotation during the closed cycle process are formed co-rotating, so that the flow energy of the working medium is essentially maintained during the closed loop process.
  • the heat exchangers each have at least one tube through which a liquid heat transfer medium flows.
  • the expansion unit connects directly to the compressor via the heat exchanger.
  • the wheels of the compressor and the expansion unit are mounted on a common rotary shaft.
  • the pressure increase of the working medium can be achieved via a centrifugal acceleration when a mitcardendes with impellers of the compressor and the expansion unit housing is provided.
  • a co-rotating heat exchanger is accommodated in the housing.
  • the co-rotating heat exchanger is circumferentially arranged outside.
  • a device results in a comparatively low overall weight, since the wall thickness of the working medium leading tubes can be made smaller than those of the working medium receiving housings.
  • the pipeline system has linear compression tubes extending in the radial direction.
  • the pipeline system has curved expansion tubes against the direction of rotation of the rotary shaft.
  • the expansion tubes can be arcuately curved in cross section for the purpose of a structurally simple design.
  • the expansion tubes it is also possible for the expansion tubes to have a curvature in cross-section with a radius that constantly reduces towards the center of rotation. This can reduce any turbulence in the piping system.
  • a flow of the working medium in the piping system is reliably ensured if, in the piping system, a blade wheel rotating relative to the piping system is included.
  • the paddle wheel which is designed as a compressor, expansion turbine or stator, be rotatably disposed, resulting in a relative movement to the rotating piping system due to the rotationally fixed arrangement.
  • the impeller is associated with a motor for generating or using a relative movement to the piping system or a generator which converts the shaft power generated by the relative movement of the impeller into electrical energy.
  • Fig. 1 schematically a process block diagram of a thermodynamic cycle is shown, as this is basically known in the prior art.
  • an isentropic compression of the gaseous working medium is initially carried out with the aid of a compressor 1.
  • isobaric heat removal takes place via a heat exchanger 2, so that the thermal energy is delivered at high temperature via a circuit (with water, water / antifreeze or other liquid heat transfer media) to a heating circuit.
  • a turbine formed relaxation unit 3 an isentropic relaxation is performed, whereby mechanical energy is recovered.
  • an isobaric heat supply is performed via a further heat exchanger 4, whereby thermal energy of low temperature is supplied to the system via a circuit (with water, water / antifreeze, brine or other liquid heat transfer media).
  • thermal energy from well water, from so-called deep probes, in which the located in a heat exchanger located up to 200 m in the ground, the heat is removed and the heat pump is supplied or the thermal energy from just under the earth lying large heat exchangers (Piping) or taken from the air.
  • an isentropic compression is again effected with the aid of the compressors 1, as described above.
  • the cycle described above takes place in the reverse order.
  • a motor 5 for driving a rotary shaft 5 ' is provided;
  • the engine is replaced by a generator 5 and motor generator 5.
  • a device in which by means of the motor 5 via the rotary shaft 5 ', a compressor 1 is driven with a co-rotating housing 6. With the driven by the electric motor 5 rotating shaft 5 'wheels 1' of the compressor 1 are also driven, so that in the closed, stationary housing 8 recorded noble gas, preferably krypton or xenon, is compressed due to the centrifugal acceleration in the co-rotating housing 6 ,
  • noble gas preferably krypton or xenon
  • a spiral-shaped pipe 9 of the heat exchanger 2 is accommodated, in which a heat exchange medium, for example water, is accommodated.
  • the comparatively cold water is introduced via an inlet 10 in the flow direction 10 'in the spiral pipe 9 and is circumferentially arranged in the co-rotating housing 6 to achieve isobaric heat removal from the working medium at the highest possible pressure of the working medium, so that at the output 11 a comparatively warm water can be removed.
  • the working medium then flows without significant flow losses to impellers 3 'of the expansion unit 3, via which mechanical energy is recovered. Subsequently, an isobaric heat supply takes place via a spiral-shaped pipe 12 of the further heat exchanger 4 in the stationary housing 8, before the working medium is again subjected to an adiabatic isentropic compression via the running wheels 1 'of the compressor 1.
  • the energy of the working medium which is accommodated in the device forming a closed system, maintains its flow energy during compression in the compressor 1 and / or during expansion in the expansion unit 3 and only via a centrifugal acceleration of the gas molecules of the working medium an increase in pressure or reduction of the working medium is achieved.
  • the efficiency or the coefficient of performance in the conversion of thermal energy of lower temperature into thermal energy of higher temperature by means of electrical or mechanical energy and vice versa can be substantially improved.
  • Fig. 3 is shown a further embodiment, in which case a stationary inner housing 6 'is provided.
  • the design complexity is simplified.
  • the stationary surfaces with which the working fluid is in communication formed as smooth as possible and there are no transverse to the flow heat transfer tubes, which would further increase the pressure loss provided .
  • the spiral-shaped pipe 9 of the heat exchanger 2 is not exposed, but received in the stationary housing 6 'with a smooth surface 2'.
  • an insulation 13 is accommodated in the interior of the stationary housing 6 '.
  • Fig. 4 a further embodiment is shown, which is essentially that of Fig. 3 corresponds and only the arrangement of the motor 5 different; Namely, in this embodiment, the motor 5 is accommodated within the fixed housing 6.
  • a further embodiment of the device according to the invention is shown, in which case all under the pressure of the working fluid parts are formed as pipes or piping system 17, whereby the total weight of the device is reduced and the wall thickness of the tubes 17 may be made smaller than that of the in the Fig. 2 to 4 shown housing 6, 6 'and 8.
  • the working fluid is first compressed in the radially extending compression tubes 18 of the piping system 17 of the compressor unit 1 due to the centrifugal acceleration.
  • the heat exchanger 2 in this case has to the outer, extending in the axial direction portion of the tubes 17 coaxially arranged tubes 19 which enclose the respective tube 17, so that the heat of the compressed working medium is discharged in countercurrent to the liquid heat exchange medium of the heat exchanger 2.
  • the expansion tubes 20 are in this case curved counter to the direction of rotation 21 of the device, which due to the rearward tube curvature (see. Fig. 7 ) reliably results in a circulation of the working medium.
  • the expansion tubes 20 can be bent in a semicircular shape, so that they can be produced in a structurally simple manner. Subsequently, the working medium flows in the axial direction in the piping system 17, in which case the low-pressure heat exchanger 4 in turn has a coaxially arranged tube 19, so that heat from the liquid heat exchange medium to the cold, relaxed working medium is delivered.
  • piping system 17 for the working medium, which are arranged offset by 90 ° to each other.
  • the piping system 17 may also have a larger number of conduits 20, only the rotational symmetry of the arrangement is to be maintained due to the ease of balancing.
  • the coaxial with the axially extending portions of the tubes 17 arranged tubes 19 of the heat exchanger 2 and 4 are connected via lines 22, 23, 24, 25 fluidly connected to each other, said conduit system 22 to 25 is fixedly connected to the other device, so that the lines 22 to 25 are carried out co-rotating.
  • the liquid heat transfer medium is supplied to the piping system 17 via an inlet 26 'of a static distributor 26; via a co-rotating manifold 27, the heat exchange medium is then supplied via the line 22 to the heat exchanger 2, in which it is heated by the line 23 in the co-rotating manifold 27 is recycled.
  • the heated heat transfer medium is then fed to the heating circuit via the static distributor 26 or a drain 26 ".
  • the cold heat exchange medium of the heat exchanger 4 is passed via an inlet 28 'of a static distributor 28, conveyed with another co-rotating distributor 29 in this co-rotating line 25 to the low-pressure heat exchanger 4, where heat is released to the gaseous working medium. Subsequently, the heat exchange medium is supplied via the co-rotating line 25 to the co-rotating distributor 29 then the static manifold 28, and finally leaves via a drain 28 '' the device.
  • a motor 5 For driving compressor 1, heat exchanger 2, 4 and relaxation unit 3, in turn, a motor 5 is provided.
  • FIGS. 8 and 9 is an embodiment similar to that of FIGS. 5 to 7 shown, but here are the expansion tubes 20 are not circular arc-shaped in cross-section, but have a continuously decreasing radius to the rotation axis center 30. As a result, a monotonically decreasing delayed movement of the working medium is achieved, whereby any turbulence can be reduced.
  • two offset by 60 ° to each other arranged independent piping 17, where per pipe system 17 three densifications, relaxations, etc. take place.
  • Fig. 10 a further embodiment is shown, which is largely that according to the FIGS. 5 to 7 corresponds, however, the circulation of the working medium is not achieved due to the direction of rotation curved tubes 20, but with the help of a paddle wheel 31, which acts as a compressor or as a turbine.
  • the impeller 31 is arranged stationary, wherein due to the relative rotational movement to the surrounding the impeller 31 tubes 17, a flow of the working medium in the tubes 17 is effected.
  • the working medium is expanded in the tubes 17 of the expansion unit 3 and the impeller 31 is fed, wherein the impeller 31 is received in a Schaufelradgephase 32, which is closed by a cover 33.
  • the impeller 31 is rotatably supported by bearings 34, however, has permanent magnets 35 which cooperate with non-rotatably mounted outside the Schaufelradgephaseuses 32 permanent magnet 36, so that the impeller 31 is arranged rotationally fixed.
  • the magnets 36 are held resting on a static shaft 37 here.
  • Fig. 11 is one to the in Fig. 10 shown embodiment very similar trained device shown, but here the relative rotational movement of the paddle wheel 31 to the tubes 17 of the compressor and relaxation unit 1 and 3 by means of a motor 38 is generated.
  • the motor 38 is rotatably connected to the co-rotating manifold 27.
  • the power supply takes place via lines 39, which are accommodated in a shaft 40.
  • the shaft 40 contacts 41.
  • the motor 5 in this embodiment only provides power to overcome the aerodynamic drag of the rotating system.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP08782795.2A 2007-07-31 2008-07-21 Verfahren zum umwandeln thermischer energie niedriger temperatur in thermische energie höherer temperatur mittels mechanischer energie und umgekehrt Active EP2183529B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL08782795T PL2183529T3 (pl) 2007-07-31 2008-07-21 Sposób przemiany energii termalnej niskiej temperatury w energię termalną wyższej temperatury przy pomocy energii mechanicznej i odwrotnie

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0120307A AT505532B1 (de) 2007-07-31 2007-07-31 Verfahren zum umwandeln thermischer energie niedriger temperatur in thermische energie höherer temperatur mittels mechanischer energie und umgekehrt
PCT/AT2008/000265 WO2009015402A1 (de) 2007-07-31 2008-07-21 Verfahren zum umwandeln thermischer energie niedriger temperatur in thermische energie höherer temperatur mittels mechanischer energie und umgekehrt

Publications (2)

Publication Number Publication Date
EP2183529A1 EP2183529A1 (de) 2010-05-12
EP2183529B1 true EP2183529B1 (de) 2017-05-24

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EP08782795.2A Active EP2183529B1 (de) 2007-07-31 2008-07-21 Verfahren zum umwandeln thermischer energie niedriger temperatur in thermische energie höherer temperatur mittels mechanischer energie und umgekehrt

Country Status (16)

Country Link
US (1) US8316655B2 (ko)
EP (1) EP2183529B1 (ko)
JP (1) JP5833309B2 (ko)
KR (1) KR101539790B1 (ko)
CN (1) CN101883958B (ko)
AT (1) AT505532B1 (ko)
AU (1) AU2008281301B2 (ko)
BR (1) BRPI0814333A2 (ko)
CA (1) CA2694330C (ko)
DK (1) DK2183529T3 (ko)
ES (1) ES2635512T3 (ko)
HU (1) HUE033411T2 (ko)
NZ (1) NZ582993A (ko)
PL (1) PL2183529T3 (ko)
RU (1) RU2493505C2 (ko)
WO (1) WO2009015402A1 (ko)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT509231B1 (de) * 2010-05-07 2011-07-15 Bernhard Adler Vorrichtung und verfahren zum umwandeln thermischer energie
EP2489839A1 (en) * 2011-02-18 2012-08-22 Heleos Technology Gmbh Process and apparatus for generating work
EP2810001B1 (de) * 2012-02-02 2019-04-10 Magna Powertrain Bad Homburg GmbH Verdichter-wärmetauscher-einheit für ein heiz-kühl-modul für ein kraftfahrzeug
AT515210B1 (de) * 2014-01-09 2015-07-15 Ecop Technologies Gmbh Vorrichtung zum Umwandeln thermischer Energie
AT515217B1 (de) * 2014-04-23 2015-07-15 Ecop Technologies Gmbh Vorrichtung und Verfahren zum Umwandeln thermischer Energie
US10578342B1 (en) * 2018-10-25 2020-03-03 Ricardo Hiyagon Moromisato Enhanced compression refrigeration cycle with turbo-compressor
CN109855913A (zh) * 2019-03-04 2019-06-07 中国地质科学院水文地质环境地质研究所 地下水放射性惰性气体核素测年采样系统及其采样方法
DE102019009076A1 (de) * 2019-12-28 2021-07-01 Ingo Tjards Kraftwerk zur Erzeugung elektrischer Energie

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Also Published As

Publication number Publication date
US20100199691A1 (en) 2010-08-12
CN101883958A (zh) 2010-11-10
AU2008281301A1 (en) 2009-02-05
PL2183529T3 (pl) 2017-10-31
JP5833309B2 (ja) 2015-12-16
JP2010534822A (ja) 2010-11-11
CN101883958B (zh) 2013-11-20
KR20100051060A (ko) 2010-05-14
HUE033411T2 (hu) 2017-12-28
BRPI0814333A2 (pt) 2015-01-20
RU2010105705A (ru) 2011-08-27
KR101539790B1 (ko) 2015-07-28
AT505532B1 (de) 2010-08-15
ES2635512T3 (es) 2017-10-04
AT505532A1 (de) 2009-02-15
RU2493505C2 (ru) 2013-09-20
US8316655B2 (en) 2012-11-27
DK2183529T3 (en) 2017-08-28
AU2008281301B2 (en) 2012-12-06
CA2694330A1 (en) 2009-02-05
CA2694330C (en) 2014-07-15
NZ582993A (en) 2011-10-28
EP2183529A1 (de) 2010-05-12
WO2009015402A1 (de) 2009-02-05

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