CA1247376A - Method of intensifying heat in reversed rankine cycle and reversed rankine apparatus for conducting the same - Google Patents
Method of intensifying heat in reversed rankine cycle and reversed rankine apparatus for conducting the sameInfo
- Publication number
- CA1247376A CA1247376A CA000479599A CA479599A CA1247376A CA 1247376 A CA1247376 A CA 1247376A CA 000479599 A CA000479599 A CA 000479599A CA 479599 A CA479599 A CA 479599A CA 1247376 A CA1247376 A CA 1247376A
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- Prior art keywords
- coolant
- temperature side
- vortex tube
- lower temperature
- exit
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P80/00—Climate change mitigation technologies for sector-wide applications
- Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
- Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply
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- Engine Equipment That Uses Special Cycles (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE:
A reversed Rankine cycle system, wherein a vortex tube is disposed between the compressor and the condenser in a reversed Rankine cycle, the superheated vapors of coolant at a high pressure discharged from the compressor are taken out while separating them by the vortex tube into higher and lower temperature components through energy separation to render most of the portion thereof into superheated vapors of coolant at a higher temperature and the remaining portions into vapors of coolant at a lower temperature respectively, and the superheated vapors of coolant separated to the higher temperature side are introduced into the circuit on the higher temperature side of the condenser and condensated therein, while the vapors of coolant separated to the lower temperature side are recycled to the system, of the cycle, preferably, to the circuit on the lower temperature side of the condenser. Heat may be supplied from the atmospheric air or from the compressor to the vapors of coolant from the lower temperature side of the vortex tube or, in the case where the temperature of the coolant on the lower tmeperature side is high, excess heat may be recovered therefrom by a heat exchanger for heat absorption.
A reversed Rankine cycle system, wherein a vortex tube is disposed between the compressor and the condenser in a reversed Rankine cycle, the superheated vapors of coolant at a high pressure discharged from the compressor are taken out while separating them by the vortex tube into higher and lower temperature components through energy separation to render most of the portion thereof into superheated vapors of coolant at a higher temperature and the remaining portions into vapors of coolant at a lower temperature respectively, and the superheated vapors of coolant separated to the higher temperature side are introduced into the circuit on the higher temperature side of the condenser and condensated therein, while the vapors of coolant separated to the lower temperature side are recycled to the system, of the cycle, preferably, to the circuit on the lower temperature side of the condenser. Heat may be supplied from the atmospheric air or from the compressor to the vapors of coolant from the lower temperature side of the vortex tube or, in the case where the temperature of the coolant on the lower tmeperature side is high, excess heat may be recovered therefrom by a heat exchanger for heat absorption.
Description
$~4'^~3~
Technical F.ield Thi~ lnvention concerns a method o~ intensifying heat in a reversed Rankine cycle, in which a vortex tube is incorpora-ted in a coolant circuit between a compressor and a conden~er in the reversed Ranklne cycle, as well as a reversed Rankine cycle apparatu~ for conducting the same.
Background Art In the reversed Rankine cycle sucll as a heat pump, the heat calorie discharged from a conden~er is generally determined by -the hea-t calorie intaken to an evaporator and the amount o.~ work of an compressor. Accordingly, conventional reversed Ranklne cycle apparatus involve~
a problem in that if the heat calorie intaken to the evaporator is con~tant, a great amount of work ha~ to be done ~y the compressor in order to increase the enthalpy in the higher temperature reglon and, in addition, no graat coefficient of performance can be attained slnce the cycle take~ a vertically e~tended configuration in the p.i diagram where the coolant is deeply brou~ht into a super-cooling region. Furthermore, if the heat-endurance of the 737~
compre~sor is restric-ted, there is an inevitable limit for increasing the amount of work in order to increase the enthalpy.
While on the other hand, there has been known a vortex tube as a device of converting a ga~ supplied under a high pressure into a vortex stream at a high veloclty, separating the same into hlgher and lower temperature components -through energy separation and diecharging them from two opposing exits. Howeve:r, the vortex tube has hitherto been used fOI' utilizing the 3eparated gas on the lower temperature side while discharging the higher temperature component to the atmosphere, and there have been known no method and apparatus for intensl~ylng heat by combining them to the reversed Rankine cycle as far as the present inventors know.
A primary object of -this invention i~ to improve the performance of heat pumps or refrigerators or coolers by separating the 3uperheated vapor~ of coolant rendered -to high pressure and high temperature by the compressor in the reversed Rankine cycle into higher and lower temperature components through energy separatlon in the vortex tube thereby further raising the temperature of most part of the superheated vapors o~ the coolant.
Another ob~ect o~ this invention is to ~urther increa~e the enthalpy, as well as protect the compressor in the rever~ed Rankine cycle by causing the heat generated '73~
from the compressor to be absorbed into the vapors of coolant separated by the vortex tube to the lower temperature side.
DISCLOSURE OF THE INVENTION
The present inventors have taken notice of the fact that most part of a gas supplied under a high pressure to a vortex tube can be taken out a-t a temperature much higher than that at the supply inlet by discharging only the slight portion of the gas at a high pressure from the exit on the lower temperature side, while discharging the remaining portion from the exit on the higher temperature side, and have accomplished this invention based on the findings that the performance of a heat pump or refrigerator (cooler) can be improved by combining the vortex tube with the reversed Rankine cycle.
According to the present invention there is provided a method of intensifying heat in a reversed Rankine cycle, which comprises:
- introducing superheated vapors oE coolant at a high pressure discharged from a compressor in a reversed Rankine cycle to the supply port of a vortex tube, - separating the superheated vapors of coolant into higher and lower temperature components through energy separation such that from 70% to 100% of the introduced superheated vapors of coolant is discharged from an exit on the higher temperature side of the vortex tube and the remaining portion thereof discharged from an exit on the lower temperature side of said vortex tube, - condensating the superheated vapors of coolant raised to a higher temperature separated to the exit on the higher temperature side of the vortex tube by a condenser in the reversed Rankine cycle, and - recycling the vapors of coolant rendered to a lower temperature separated to the exit on the lower temperature side of -the vortex tube -to the system of the reversed Rankine cycle.
Preferably, the method comprises introducing superheated vapors of coolant at a high pressure into a vortex tube while connecting a coolan~ circuit on the discharging side of a compressor in the reversed Rankine cycle to the supply inlet for pressurized gas of the vortex tube, discharging from 95% to 98% of the introduced superheated vapors of coolant from the exit on -the higher temperature side of the vortex tubes while discharging the remaining portion from the exit on the lo~er temperature side theraof, thereby separating to take out from 95% to 9~%
of the superheated vapors of coolant at a higher temperature and taking out the remaining portion at a lower temperature, condensating the superheated vapors of coolant separated on the higher temperature side by the condenser in the reversed Rankine cycle while recycling the vapors of coolant separated on the lower temperature side to the system of the reversed Rankine cycle, particularly, to the coolant circuit on the lower temperature side of the condenser.
Thus, the coolant discharged from the exit on the lower temperature side of vortex tube may further be circulated under the supply of heat from the external atmosphere or the compressor, or it may be recycled to the system of the cycle after recoverying a portion of heat in a case where the temperature of the coolant is higher than required.
According to the present invention, there is also provided a reversed Rankine cycle apparatus wherein coolant is recycled as an operational fluid, comprising:
- at least one vortex tube, in which from 70% to 100% of a gas introduced at a high pressure is discharged from an exit on the higher temperature side of the vortex '737~
tube and the remaining portion is discharged from an exit on the lower temperature side of the vortex tube to thereby separate said introduced gas into higher and lower temperature components through energy separation, wherein - a coolant circuit on the discharging side of a first compressor in the reversed ~ankine cycle is connected to a supply port for pressurized gas of the vortex tube, a coolant circuit on the higher tempexature side of a second condenser in the reversed Rankine cycle is connected to the exit on the higher temperature side of the vortèx tube, and the exit on -the lower temperature side of the vortex tube is connected with the coolant circuit on the lower temperature side oE said second condenser by means of a circuit.
BRIEF DESCRIPTION OF THE D~AWINGS:
Figure 1 is a flow chart showing the basic constitution of this invention, Figure 2 is an exploded view for a preferred vortex tube, Figure 3 is a longitudinal cross sectional view taken in an axial direction of the vortex tube shown in Figure 2, /
/
- ~a -~ ~ ~ 7 3 t~
~ igure 4 is a p.i. diagram o~ the reversed Ran1~ine cycle according to this invention, and Figure 5 through Figure 9 respectively show ~low charts for o-ther embodiments according to this invention respectively.
Best Mode for Carrying Out the Invention This invention will now be described by way o~
embodiments referring to -the accompanying drawings.
~ igure 1 is a ~low chart showing the basic constitution of the reversed Rankine cycle according to this invention.
In a reversed Rankine cycle in which coolant, for example, fron 22 as an opera-tional fluid is recycled through the path : evaporator 1 ~ compressor 2 ~ condenser 4 ~ liquid receiver 5 ~ restriction valve 6 ~ evaporator 1, a vortex tube 3 ~or the energy separation o~ superheated vapors of coolant discharged from the compressor 2 into higher and lower tempera-ture components is incorporated between the compressor 2 and the condenser 4. Speci~lcally, as sho~n in the figure, a coolant circuit 2' on the discharging side o~ the compressor 2 is connected to -the supply inlet 3a for high pressure gas o~ the vortex tube 3, and the coolant circuit 4a on the higher temperature side of the condenser 4 is connected to the exit 3b on the higher temperature side of the vortex tube 3, while the exit 3c on the lower temperature side of the vortex tube 3 is '737~
connected to the system of the reversed Rankine cycle, part~cularly, to -the coolant circuit 4b on the lower tempera-ture side of the condenser 4 by way of a circuit 7, The vortex tube 3 is adjusted for the flow rate such tha-t from about 95 % to 98 % of the s-uperheated vapors of coolant sent from -the supply port 3a is discharged from the coolant exit 3b on the higher temperature side, while the remaining portion ls discharged from -the coolant exit 3c on the lower tempe:ra-ture side.
Figure 2 and Figure 3 exemplify a preferred vortex tube for use in this invention. The vortex tube 3 comprises a hollow casing 31 having a hollow cylindrical portion therein extended in the axial direction and having a supply inlet 3a for pressurized gas in communication with the inside of the hollow cylinder, a high temperature gas flow tube 32 of a diameter smaller than the inner diameter of the cylinder of the casing 3 connected to one axial opening end of the casing and a circular vortex generation devlce 33 having a through hole 33 perforated in the axial center and fitted in the cylindrical hollow portion of the casing 31.
The vortex generatlon device 33 has a recess 33b at the center of its end opposing to the high temperature gas flow tube 32, in which a plurality of grooves 33d extending slantwise or curvelinearly to the radial direction are engraved in a protruding circular edge 33c formed around 737~
the periphery o~ the recess 33b, and the device is disposed within the casing 31 such that the grooYes 33d are opposed to the gas flow tube 32 and the upper ends of the groo~es 33d are in communicatlon with -the gas supply por-t 3a o~
the casing 31.
A hollow sealing cap 35 is threadingly coupled ~roM
behind the vortex generation device 33 by way o~ an o-ring 34 and the top end thereo~ is abutted against the rear portion of the vortex genera-tion device 33 to secure -the device 33.
In this way, a pressuri2ed gas supplied at a high velocity from the gas inlet to the inside o~ the casing 31 is converted into a vortex stream under the rotation at a high velocity by the vortex generation device 33 to cause temperature change therein, by which a gas at a higher temperature is discharged ~rom the exit 3b of the high temperature gaæ flow tube 32, while a gas at a lower temperature is discharged through the axial center hole 33a o~ the vortex generation device 33 in the direc-tion opposite to that o~ the higher temperature ~low tube. The vortex tube 3 shown in the drawing partlcularly has the following ~eatures.
Speci~ically, as shown in Figure 3, a gap 36 is disposed between the -top end o~ the vortex generation device 33 disposed within the casing 31 and the inner end of the hollow casing 31 in continuous with the high 37~
tempera-ture gas flow tube 32, and the inner circumferential surface 37 of the casing opposing to the gap 36 is tapered toward the communication port of the high temperature gas ~low tube 32.
The tapered surface on the i.nner circumferential surface 37 of the casing is preferably formed with such an uniform angle -that the apex of the taper cone defines the degree of 90 .
The top end of -the high temperature gas flow tube 32 may be coupled with a heat dissipation member 40 having a plurality of discharge apertures 3~ formed at the circum-ferential wall thereof and threadingly engaged with a cap 39 at the end thereof, or a discharge control screw 41 for higher and lower temperature gases may be attached retractably from the central aperture of the cap 39 to the inside of the heat dissipation member L~o.
In the figure, reference 42 denotes a brak~ng member comprising a spiral member 42a whose both ends 42b and 42c are bent in the diametrical direction o~ the spiral member 42a.
While the vortex tube as shown in Figure 2 and Figure 3 has much more excellent performance due to the above-described feature as compared with the conventional ones, the vortex tube for use in this invention is no way limited to the illustrated embodiment but it is of course possible to use any of known tubes.
7~7~
In any case, the compressor 1 and -the vortex tube 3 are constituted such that the performance of the compressor 1 may not be impaired and a Yortex stream at a ~low velocity requi:red for -the separation into higher and lower temperature components is generated in the vortex -tube 3.
In the vortex tube 3, temperature rise in the coolant on the higher temperature side is increased where the flow rate ratio is relatively grea-ter at the exit 3b on the side of the higher temperature and the temperature ~all on the lower temperature side is increased correspondingly, that is, the tempera-ture difference relative to the lower temperature side is enlarged as the ~low rate ratio on the side of the higher temperature is made greater. Accordingly, in order -to improve the coefficient of per~ormance of the reversed Rankine cycle according to this invention when used as a hea-t pump or a refrigerator, it is advantageous to set -the flow rate ratio in the exit 3b on the higher temperature side and that in the exit 3c on the lower temperature side such that the temperature difference between the coolant on the higher -temperature side and the coolant on the lower temperature side of the vortex tube 3 is as large as possible. As the result o~ the experiment, it has been found in this invention that it is advantageous for improving the coefficient of performance to adjust the flow rate ratio on the higher temperature side to between about 95 % and g8 ~ and, accordingly, to adjust the flow rate -ratio on the lower temperature side to be-tween about 5 % and 2 % of the vortex tube 3 incorporated in the reversed Rankine cycle.
Figure 4 shows the p.i diagram in a case where the reversed Rankine cycle apparatus shown in ~igure 1 is used as a heat pump cycle and, particularly, this re].ates to the case where the temperature of the coolant separated on the lower temperature side of the vortex tube is lower than the external temperature. The flgure is shown as an ideal cycle not considering the frictional loss.
The opera~ion of the reversed Rankine cycle according to this invention will now be described based on ~igure 1 and Figure 4.
Coolant subjected to isentropic expansion through the restriction valve 6 or the like (Figure 4, 6-1) evaporates isothermally while taking external heat in the evaporator 1 to increase the enthalpy and is then sucked into the compressor (Figure 4, 1-2).
The coolant is compressed adiabatically in the compreæsor 2 into superheated vapors at high pressure and high temperature and then introduced to the supply port 3a of the vortex tube 3 (~igure 4, 2-3).
The coolant supplied under a high pressure to the vortex tube 3 is separated depending on a predetermined ~low rate ratio (~or instance, 97 ~ on the higher " ~73~
temperature side and 3 % on the lower temperature æide) due to the characteris-tics o.~ the vortex tube 3, and the coolant separated -to -the exit 3b on the higher tempera-ture side is increased with the enthalpy and the stagnation point pressure (Figure 4, 3-4).
The coolant on the higher temperature side whose temperature rises in the vortex tube 3 is subjected to the isobaric condensa-tion in the condenser 4 to release the heat calorie possessed therein (Figure 4, 4-5).
While on the other hand, the coolant ~eparated to -the exit 3c on the lower temperature side o~ the vortex tube 3 is decreased with the enthalpy and the pressure (Figure 4, 3-7).
The coolant on -the higher -temperature side after the condensation is reduced with the pressure by the admixture with the coolant on the lower temperature side to increase the enthalpy (Figure 4, 5-6). At the same time, the coolant on the lower temperature side is reduced with the enthalpy in admixture with the coolant on the higher temperature side to recover the pressure. Particularly, in a case where the temperature o~ the coolant on the lower temperature side o~ the vortex tube 3, that is, the temperature o~ the coolant in -the circuit 7 is lower than the atmospheric temperature in the constitution o~ Figure 1, since the coolant on the lower temperature side absorbs external heat in the circuit 7 to increase the enthalpy ~737Çi (Figure 4, 7-8) and is then mi.xed with the coolan-t on the higher temperature side, -the entire coolant at the inlek of a throt-tling valve G is subjected to throttling expansion while havlng a further increased enthalpy than that at the kime of completing the condensat-lon for the coolant on the high temperature side (Flgure 4, 6-1).
Accordingly, the entire mixed coolant is subjected to the throttling expansion at a point where the enthalpy i8 increased than tha-t upon completion of the condensa-tion ~or the coolant on the high tempera-ture side.
Figure 5 through Figure 9 show other embodiments according to this invention. Specifically, in the embodiment shown in Figure 5, a heat exchanger 9 is disposed in the coolant circuit 7 on the lower temperature side of the vortex tube 3 for supplying hea-t -to the coolant on the lower temperature side and, since the enthalpy of -the coolant after the mixing can be further increased, it is advantageous in the case of utilizing as a heat pump cycle.
Figure 6 shows an embodiment in which the heat exchanger 9 in the embodiment of Figure 5 is disposed around the outer circumference of the compressor 2 to utilize the sur~ace temperature of the compressor 2 as the heat source for the heat exchanger 9, and it has duplicate merits of requiring no par-ticular circuit to recycle a heat source for the heat exchanger 9 and capable of ~'~4'73~
cooling the compressor 2 as well.
Further, in a case where the temperature of the coolant in -the circuit 7 is ra-ther high, the heat exchange:r 9 for supplying -the heat may be replaced with a heat exchanger 9' disposed for the heat ab~orption in the circ~lit 7 as shown in Figure 7~ In this embodiment, the heat of the coolant in the circuit 7 can directly be utilized for the warming use when applied as a heat pump cycle, as well as the -temperature o~ the coolant after the condensation can be lowered to improve the refrigerating effect when it is operated as a refrigerating cycle.
Although, embodlments having a single vortex tube incorporated to the system of the reversed Rankine cycle have been shown in Figure 1 and Figure 5 through Figure 7 for the simplicity of the explanation, this invention also includes the case of using a plurality of vortex tubes in parallel or in series in one system.
Figure 8 shows an embodiment wherein a plurality of vortex tubes 3 are combined in parallel with each other.
In this embodiment, a circuit 10 in direct connection from the compressor 2 to the condenser 4 is disposed by way of a switching valve 11, whereby it can be operated while being directly switched to a conventional appara-tus in a case if the vortex tube 3 or the like should be failed.
Figure 9 shows an embodiment, wherein exits for the higher temperature coolant of primary vortex tubes 3 and 37~
the supply port3 3a' o~ secondary vor-tex tubes 3' are communicated by means o~ pipes into serial type composite vortex tubes, and the coolant circuit 4a on the higher temperature side of the condenser 4 i8 connected to the exits ~or higher temperature coolant o~ the secondary or downstream vortex tubes, and all of the exits ~or the lower temperature coolant o~ -the vortex tubes are connected to the coolant circuit 4b o~ the lower temperature side o~
the condenser 4. The embodiment shown in Figure 9 has an effect o~ raising the coolant temperature to a further higher temperature.
Description will now be made for the test example in which the apparatus according to -this invention is used ~or the warming opera-tion as a heat pump.
Test example tl) Heat Pump Kind of the coolant : Fron 22 Conditions ~or the coolant Discharging capacity o~ the compressor piston = 46 m3/hour Coolant recycling amount G = 301 kg/hour (assuming volume e~iciency = 0.85) Compressor rated power = 7.5 kW/hour Vortex Tube Twelve vortex tubes each adjusted to about 97 % of ~low rate ratio at the exit 3b for higher temperature coolant and to about 3 % o~ ~low rate ratio at the exit 3c ~247376 for lower temperature coolant were dispo~ed in parallel.
The pipe 7 for the coolant on the lower kemperature ~ide was connected directly to -the coolant circuit 4b on the lower temperature side of -the condenser 4 as in the embodiment shown in Figure 1.
Heat source section Water at 16 C wa~ supplied at the flow rate of 15 ~min to -the evaporator to conduct heat exchange Heat dissipating section Water at 16 C was recycled at the flow rate of 30 Q/min to the conden~er to conduct heat exchange
Technical F.ield Thi~ lnvention concerns a method o~ intensifying heat in a reversed Rankine cycle, in which a vortex tube is incorpora-ted in a coolant circuit between a compressor and a conden~er in the reversed Ranklne cycle, as well as a reversed Rankine cycle apparatu~ for conducting the same.
Background Art In the reversed Rankine cycle sucll as a heat pump, the heat calorie discharged from a conden~er is generally determined by -the hea-t calorie intaken to an evaporator and the amount o.~ work of an compressor. Accordingly, conventional reversed Ranklne cycle apparatus involve~
a problem in that if the heat calorie intaken to the evaporator is con~tant, a great amount of work ha~ to be done ~y the compressor in order to increase the enthalpy in the higher temperature reglon and, in addition, no graat coefficient of performance can be attained slnce the cycle take~ a vertically e~tended configuration in the p.i diagram where the coolant is deeply brou~ht into a super-cooling region. Furthermore, if the heat-endurance of the 737~
compre~sor is restric-ted, there is an inevitable limit for increasing the amount of work in order to increase the enthalpy.
While on the other hand, there has been known a vortex tube as a device of converting a ga~ supplied under a high pressure into a vortex stream at a high veloclty, separating the same into hlgher and lower temperature components -through energy separation and diecharging them from two opposing exits. Howeve:r, the vortex tube has hitherto been used fOI' utilizing the 3eparated gas on the lower temperature side while discharging the higher temperature component to the atmosphere, and there have been known no method and apparatus for intensl~ylng heat by combining them to the reversed Rankine cycle as far as the present inventors know.
A primary object of -this invention i~ to improve the performance of heat pumps or refrigerators or coolers by separating the 3uperheated vapor~ of coolant rendered -to high pressure and high temperature by the compressor in the reversed Rankine cycle into higher and lower temperature components through energy separatlon in the vortex tube thereby further raising the temperature of most part of the superheated vapors o~ the coolant.
Another ob~ect o~ this invention is to ~urther increa~e the enthalpy, as well as protect the compressor in the rever~ed Rankine cycle by causing the heat generated '73~
from the compressor to be absorbed into the vapors of coolant separated by the vortex tube to the lower temperature side.
DISCLOSURE OF THE INVENTION
The present inventors have taken notice of the fact that most part of a gas supplied under a high pressure to a vortex tube can be taken out a-t a temperature much higher than that at the supply inlet by discharging only the slight portion of the gas at a high pressure from the exit on the lower temperature side, while discharging the remaining portion from the exit on the higher temperature side, and have accomplished this invention based on the findings that the performance of a heat pump or refrigerator (cooler) can be improved by combining the vortex tube with the reversed Rankine cycle.
According to the present invention there is provided a method of intensifying heat in a reversed Rankine cycle, which comprises:
- introducing superheated vapors oE coolant at a high pressure discharged from a compressor in a reversed Rankine cycle to the supply port of a vortex tube, - separating the superheated vapors of coolant into higher and lower temperature components through energy separation such that from 70% to 100% of the introduced superheated vapors of coolant is discharged from an exit on the higher temperature side of the vortex tube and the remaining portion thereof discharged from an exit on the lower temperature side of said vortex tube, - condensating the superheated vapors of coolant raised to a higher temperature separated to the exit on the higher temperature side of the vortex tube by a condenser in the reversed Rankine cycle, and - recycling the vapors of coolant rendered to a lower temperature separated to the exit on the lower temperature side of -the vortex tube -to the system of the reversed Rankine cycle.
Preferably, the method comprises introducing superheated vapors of coolant at a high pressure into a vortex tube while connecting a coolan~ circuit on the discharging side of a compressor in the reversed Rankine cycle to the supply inlet for pressurized gas of the vortex tube, discharging from 95% to 98% of the introduced superheated vapors of coolant from the exit on -the higher temperature side of the vortex tubes while discharging the remaining portion from the exit on the lo~er temperature side theraof, thereby separating to take out from 95% to 9~%
of the superheated vapors of coolant at a higher temperature and taking out the remaining portion at a lower temperature, condensating the superheated vapors of coolant separated on the higher temperature side by the condenser in the reversed Rankine cycle while recycling the vapors of coolant separated on the lower temperature side to the system of the reversed Rankine cycle, particularly, to the coolant circuit on the lower temperature side of the condenser.
Thus, the coolant discharged from the exit on the lower temperature side of vortex tube may further be circulated under the supply of heat from the external atmosphere or the compressor, or it may be recycled to the system of the cycle after recoverying a portion of heat in a case where the temperature of the coolant is higher than required.
According to the present invention, there is also provided a reversed Rankine cycle apparatus wherein coolant is recycled as an operational fluid, comprising:
- at least one vortex tube, in which from 70% to 100% of a gas introduced at a high pressure is discharged from an exit on the higher temperature side of the vortex '737~
tube and the remaining portion is discharged from an exit on the lower temperature side of the vortex tube to thereby separate said introduced gas into higher and lower temperature components through energy separation, wherein - a coolant circuit on the discharging side of a first compressor in the reversed ~ankine cycle is connected to a supply port for pressurized gas of the vortex tube, a coolant circuit on the higher tempexature side of a second condenser in the reversed Rankine cycle is connected to the exit on the higher temperature side of the vortèx tube, and the exit on -the lower temperature side of the vortex tube is connected with the coolant circuit on the lower temperature side oE said second condenser by means of a circuit.
BRIEF DESCRIPTION OF THE D~AWINGS:
Figure 1 is a flow chart showing the basic constitution of this invention, Figure 2 is an exploded view for a preferred vortex tube, Figure 3 is a longitudinal cross sectional view taken in an axial direction of the vortex tube shown in Figure 2, /
/
- ~a -~ ~ ~ 7 3 t~
~ igure 4 is a p.i. diagram o~ the reversed Ran1~ine cycle according to this invention, and Figure 5 through Figure 9 respectively show ~low charts for o-ther embodiments according to this invention respectively.
Best Mode for Carrying Out the Invention This invention will now be described by way o~
embodiments referring to -the accompanying drawings.
~ igure 1 is a ~low chart showing the basic constitution of the reversed Rankine cycle according to this invention.
In a reversed Rankine cycle in which coolant, for example, fron 22 as an opera-tional fluid is recycled through the path : evaporator 1 ~ compressor 2 ~ condenser 4 ~ liquid receiver 5 ~ restriction valve 6 ~ evaporator 1, a vortex tube 3 ~or the energy separation o~ superheated vapors of coolant discharged from the compressor 2 into higher and lower tempera-ture components is incorporated between the compressor 2 and the condenser 4. Speci~lcally, as sho~n in the figure, a coolant circuit 2' on the discharging side o~ the compressor 2 is connected to -the supply inlet 3a for high pressure gas o~ the vortex tube 3, and the coolant circuit 4a on the higher temperature side of the condenser 4 is connected to the exit 3b on the higher temperature side of the vortex tube 3, while the exit 3c on the lower temperature side of the vortex tube 3 is '737~
connected to the system of the reversed Rankine cycle, part~cularly, to -the coolant circuit 4b on the lower tempera-ture side of the condenser 4 by way of a circuit 7, The vortex tube 3 is adjusted for the flow rate such tha-t from about 95 % to 98 % of the s-uperheated vapors of coolant sent from -the supply port 3a is discharged from the coolant exit 3b on the higher temperature side, while the remaining portion ls discharged from -the coolant exit 3c on the lower tempe:ra-ture side.
Figure 2 and Figure 3 exemplify a preferred vortex tube for use in this invention. The vortex tube 3 comprises a hollow casing 31 having a hollow cylindrical portion therein extended in the axial direction and having a supply inlet 3a for pressurized gas in communication with the inside of the hollow cylinder, a high temperature gas flow tube 32 of a diameter smaller than the inner diameter of the cylinder of the casing 3 connected to one axial opening end of the casing and a circular vortex generation devlce 33 having a through hole 33 perforated in the axial center and fitted in the cylindrical hollow portion of the casing 31.
The vortex generatlon device 33 has a recess 33b at the center of its end opposing to the high temperature gas flow tube 32, in which a plurality of grooves 33d extending slantwise or curvelinearly to the radial direction are engraved in a protruding circular edge 33c formed around 737~
the periphery o~ the recess 33b, and the device is disposed within the casing 31 such that the grooYes 33d are opposed to the gas flow tube 32 and the upper ends of the groo~es 33d are in communicatlon with -the gas supply por-t 3a o~
the casing 31.
A hollow sealing cap 35 is threadingly coupled ~roM
behind the vortex generation device 33 by way o~ an o-ring 34 and the top end thereo~ is abutted against the rear portion of the vortex genera-tion device 33 to secure -the device 33.
In this way, a pressuri2ed gas supplied at a high velocity from the gas inlet to the inside o~ the casing 31 is converted into a vortex stream under the rotation at a high velocity by the vortex generation device 33 to cause temperature change therein, by which a gas at a higher temperature is discharged ~rom the exit 3b of the high temperature gaæ flow tube 32, while a gas at a lower temperature is discharged through the axial center hole 33a o~ the vortex generation device 33 in the direc-tion opposite to that o~ the higher temperature ~low tube. The vortex tube 3 shown in the drawing partlcularly has the following ~eatures.
Speci~ically, as shown in Figure 3, a gap 36 is disposed between the -top end o~ the vortex generation device 33 disposed within the casing 31 and the inner end of the hollow casing 31 in continuous with the high 37~
tempera-ture gas flow tube 32, and the inner circumferential surface 37 of the casing opposing to the gap 36 is tapered toward the communication port of the high temperature gas ~low tube 32.
The tapered surface on the i.nner circumferential surface 37 of the casing is preferably formed with such an uniform angle -that the apex of the taper cone defines the degree of 90 .
The top end of -the high temperature gas flow tube 32 may be coupled with a heat dissipation member 40 having a plurality of discharge apertures 3~ formed at the circum-ferential wall thereof and threadingly engaged with a cap 39 at the end thereof, or a discharge control screw 41 for higher and lower temperature gases may be attached retractably from the central aperture of the cap 39 to the inside of the heat dissipation member L~o.
In the figure, reference 42 denotes a brak~ng member comprising a spiral member 42a whose both ends 42b and 42c are bent in the diametrical direction o~ the spiral member 42a.
While the vortex tube as shown in Figure 2 and Figure 3 has much more excellent performance due to the above-described feature as compared with the conventional ones, the vortex tube for use in this invention is no way limited to the illustrated embodiment but it is of course possible to use any of known tubes.
7~7~
In any case, the compressor 1 and -the vortex tube 3 are constituted such that the performance of the compressor 1 may not be impaired and a Yortex stream at a ~low velocity requi:red for -the separation into higher and lower temperature components is generated in the vortex -tube 3.
In the vortex tube 3, temperature rise in the coolant on the higher temperature side is increased where the flow rate ratio is relatively grea-ter at the exit 3b on the side of the higher temperature and the temperature ~all on the lower temperature side is increased correspondingly, that is, the tempera-ture difference relative to the lower temperature side is enlarged as the ~low rate ratio on the side of the higher temperature is made greater. Accordingly, in order -to improve the coefficient of per~ormance of the reversed Rankine cycle according to this invention when used as a hea-t pump or a refrigerator, it is advantageous to set -the flow rate ratio in the exit 3b on the higher temperature side and that in the exit 3c on the lower temperature side such that the temperature difference between the coolant on the higher -temperature side and the coolant on the lower temperature side of the vortex tube 3 is as large as possible. As the result o~ the experiment, it has been found in this invention that it is advantageous for improving the coefficient of performance to adjust the flow rate ratio on the higher temperature side to between about 95 % and g8 ~ and, accordingly, to adjust the flow rate -ratio on the lower temperature side to be-tween about 5 % and 2 % of the vortex tube 3 incorporated in the reversed Rankine cycle.
Figure 4 shows the p.i diagram in a case where the reversed Rankine cycle apparatus shown in ~igure 1 is used as a heat pump cycle and, particularly, this re].ates to the case where the temperature of the coolant separated on the lower temperature side of the vortex tube is lower than the external temperature. The flgure is shown as an ideal cycle not considering the frictional loss.
The opera~ion of the reversed Rankine cycle according to this invention will now be described based on ~igure 1 and Figure 4.
Coolant subjected to isentropic expansion through the restriction valve 6 or the like (Figure 4, 6-1) evaporates isothermally while taking external heat in the evaporator 1 to increase the enthalpy and is then sucked into the compressor (Figure 4, 1-2).
The coolant is compressed adiabatically in the compreæsor 2 into superheated vapors at high pressure and high temperature and then introduced to the supply port 3a of the vortex tube 3 (~igure 4, 2-3).
The coolant supplied under a high pressure to the vortex tube 3 is separated depending on a predetermined ~low rate ratio (~or instance, 97 ~ on the higher " ~73~
temperature side and 3 % on the lower temperature æide) due to the characteris-tics o.~ the vortex tube 3, and the coolant separated -to -the exit 3b on the higher tempera-ture side is increased with the enthalpy and the stagnation point pressure (Figure 4, 3-4).
The coolant on the higher temperature side whose temperature rises in the vortex tube 3 is subjected to the isobaric condensa-tion in the condenser 4 to release the heat calorie possessed therein (Figure 4, 4-5).
While on the other hand, the coolant ~eparated to -the exit 3c on the lower temperature side o~ the vortex tube 3 is decreased with the enthalpy and the pressure (Figure 4, 3-7).
The coolant on -the higher -temperature side after the condensation is reduced with the pressure by the admixture with the coolant on the lower temperature side to increase the enthalpy (Figure 4, 5-6). At the same time, the coolant on the lower temperature side is reduced with the enthalpy in admixture with the coolant on the higher temperature side to recover the pressure. Particularly, in a case where the temperature o~ the coolant on the lower temperature side o~ the vortex tube 3, that is, the temperature o~ the coolant in -the circuit 7 is lower than the atmospheric temperature in the constitution o~ Figure 1, since the coolant on the lower temperature side absorbs external heat in the circuit 7 to increase the enthalpy ~737Çi (Figure 4, 7-8) and is then mi.xed with the coolan-t on the higher temperature side, -the entire coolant at the inlek of a throt-tling valve G is subjected to throttling expansion while havlng a further increased enthalpy than that at the kime of completing the condensat-lon for the coolant on the high temperature side (Flgure 4, 6-1).
Accordingly, the entire mixed coolant is subjected to the throttling expansion at a point where the enthalpy i8 increased than tha-t upon completion of the condensa-tion ~or the coolant on the high tempera-ture side.
Figure 5 through Figure 9 show other embodiments according to this invention. Specifically, in the embodiment shown in Figure 5, a heat exchanger 9 is disposed in the coolant circuit 7 on the lower temperature side of the vortex tube 3 for supplying hea-t -to the coolant on the lower temperature side and, since the enthalpy of -the coolant after the mixing can be further increased, it is advantageous in the case of utilizing as a heat pump cycle.
Figure 6 shows an embodiment in which the heat exchanger 9 in the embodiment of Figure 5 is disposed around the outer circumference of the compressor 2 to utilize the sur~ace temperature of the compressor 2 as the heat source for the heat exchanger 9, and it has duplicate merits of requiring no par-ticular circuit to recycle a heat source for the heat exchanger 9 and capable of ~'~4'73~
cooling the compressor 2 as well.
Further, in a case where the temperature of the coolant in -the circuit 7 is ra-ther high, the heat exchange:r 9 for supplying -the heat may be replaced with a heat exchanger 9' disposed for the heat ab~orption in the circ~lit 7 as shown in Figure 7~ In this embodiment, the heat of the coolant in the circuit 7 can directly be utilized for the warming use when applied as a heat pump cycle, as well as the -temperature o~ the coolant after the condensation can be lowered to improve the refrigerating effect when it is operated as a refrigerating cycle.
Although, embodlments having a single vortex tube incorporated to the system of the reversed Rankine cycle have been shown in Figure 1 and Figure 5 through Figure 7 for the simplicity of the explanation, this invention also includes the case of using a plurality of vortex tubes in parallel or in series in one system.
Figure 8 shows an embodiment wherein a plurality of vortex tubes 3 are combined in parallel with each other.
In this embodiment, a circuit 10 in direct connection from the compressor 2 to the condenser 4 is disposed by way of a switching valve 11, whereby it can be operated while being directly switched to a conventional appara-tus in a case if the vortex tube 3 or the like should be failed.
Figure 9 shows an embodiment, wherein exits for the higher temperature coolant of primary vortex tubes 3 and 37~
the supply port3 3a' o~ secondary vor-tex tubes 3' are communicated by means o~ pipes into serial type composite vortex tubes, and the coolant circuit 4a on the higher temperature side of the condenser 4 i8 connected to the exits ~or higher temperature coolant o~ the secondary or downstream vortex tubes, and all of the exits ~or the lower temperature coolant o~ -the vortex tubes are connected to the coolant circuit 4b o~ the lower temperature side o~
the condenser 4. The embodiment shown in Figure 9 has an effect o~ raising the coolant temperature to a further higher temperature.
Description will now be made for the test example in which the apparatus according to -this invention is used ~or the warming opera-tion as a heat pump.
Test example tl) Heat Pump Kind of the coolant : Fron 22 Conditions ~or the coolant Discharging capacity o~ the compressor piston = 46 m3/hour Coolant recycling amount G = 301 kg/hour (assuming volume e~iciency = 0.85) Compressor rated power = 7.5 kW/hour Vortex Tube Twelve vortex tubes each adjusted to about 97 % of ~low rate ratio at the exit 3b for higher temperature coolant and to about 3 % o~ ~low rate ratio at the exit 3c ~247376 for lower temperature coolant were dispo~ed in parallel.
The pipe 7 for the coolant on the lower kemperature ~ide was connected directly to -the coolant circuit 4b on the lower temperature side of -the condenser 4 as in the embodiment shown in Figure 1.
Heat source section Water at 16 C wa~ supplied at the flow rate of 15 ~min to -the evaporator to conduct heat exchange Heat dissipating section Water at 16 C was recycled at the flow rate of 30 Q/min to the conden~er to conduct heat exchange
(2) Atmospheric temperature : 15 C
(3) The pressure and the temperature o~ the coolant in each o~ the states within the heat pump system during operation o~ the apparatus were as below :
__ __ _ __ __ Presæure(G) Tempera-kg/cm2ture ( C) Evaporator evaporation ¦ 0.9 -28 temperature .. .. .... _ _ Compressor suction side 0.9 5 discharge side13.2 97 _. . ..... _ .. . _ .
supply port13.2 95 exit for high13.2 131 Vortex tube temperature gas exit for low8.5 15 . ~ temperature gas _ _ __ ~ A ~Wf~
r , r j inlet Z 12.7 131 Condenser l , , ¦outlet 1 12.7 ' 36 _ __ _ _,_ _ _ _ . . ._._ l, ._.. . . _, ... , _~ ,. . .. . ....
Expansion inlet 1 12.7 ~ 5 valve loutlet ~ 0.9 1 -28 ~ L~
Further, water at 16 C supplied as the heat source (15 Q/min) to the e-vaporator 1 was cooled to water at 6 C, while water at 16 C supplied to -the condenser (30 Q/min) was warmed -to 74 C and then discharged.
Accordingly, the hea-t calorie emitted from the condenser was :
(74 -16) C x 30 Q x 60 min = 104,400 kcal/hour, and the heat calorie taken from the heat source was :
(16 - 6) C x 15 Q x 60 min = 9,000 kcal/hour Since -the heat calorie obtainable from the amount of work is : 7.5 kW x 860 kcal/hour = 6450 kcal/hour, and the rated input of the compressor used is 7.5 kW, the coeffi-cient of performance determined actually in the refrige-rating cycle of the present test example is represented based on the rated input of the compressor as :
- = ~ = 16.2 7.5 (kW) x 860 (kcal/hour) 6450 Industrial Applicability According to the reversed Rankine cycle apparatus of this lnvention, since the most portion of the superheated 737~
vapors of coolant rendered to high pressure and high tempera-ture in -the compressor is condensated after being raised to a higher tempera-ture by the vortex tube, the heat exchanging efficiency in the condenser can be improved to take out heat at higher -tempera-tureO
Specifically, the coefficient of performance h f the reversed ~ankine cycle apparatus according to this invention, when it is used as the heat pump cycle is determined based on the embodiment in Figure 4 as :
m(i3 - i6) m((i4 - i3) ~ (i6 - i5)) h + ~~ ~ ...(equation 1) i3 - i2 i3 - i2 (where m is a flow rate ratio flowing to the higher temperature side of the vortex tube, which ls smaller than 1). As compared with the coefficient of performance in the conventional heat pump cycle, it is increased by about ;
((i4 - i3) ~ (i6 - i5)) i3 - i2 in the case of m - 1. Accordingly, as already described above, since the operation is carried out, in the reversed Rankine cycle according to this invention, while setting the flow rate ratio for the coolant on the higher tempera-ture side at, preferably, from about 95 % to 9~ %, the coefficient of performance can be improved significantly.
In order to increase the entropy of -the coolant to -the same state as tha-t shown in ~igure 4 only by a compressor as in the usual case, the compressor has to ~Z473~
perform a great amount of work to result in problems in view of the heat durability and the eleckric power consumption thereo~, In addition, the p,i diagram take~
a vertically ex-tended configuration to provide a difficulty in the -throttling expansion failing to obtain desired coefficient of performance. ~hile on the other hand, according to this invention, no such problems are cau~ed since the enthalpy of the coolant discharged from the compressor is increased by the vortex tube. Further, since the coolant on the lower temperature side of the vortex tube can also get the energy in -the circuit 7 from the external atmosphere or from the heat source of the hea-t exchanger, a further contribution can be made to the improvement in the coefficient of performance. Further-more, since the relationship between the coefficient of performance ~h as the heat pump cycle and the coefficient o~ performance ~c as the refrigerator cycle is expressed as : ~c = ~h ~ 1, the improvement in the coefficient of performance of the heat pump cycle just means the improvement in the coef~icient of performance in the refrigerator cycle and, accordingly, this invention can improve the performance when it is used both to -the heat pump and to the refrigerator.
In the embodiment shown in Figure ~ and Figure 6, since the coolant on the lower temperature side of the vortex tube absorbs heat by means of the heat exchanger ~737~
and -then mixed with the coolant on -the higher temperature side, the enthalpy (i6 - i5) in the above mentioned equation 1 is increased and, accordingly, the coe~icienk o~ perfo:rmance when it is used as the heat pump can further be improved. Particularly, in the embodiment shown in Figure 6, ~ince the outer circumference of the compres~or ls used as the hea-t exchanglng section in the circuit 7 where the hea-t at the outer circumference o~ the compressor raised -to a higher temperature ls absorbed, it has a merit of requiring no particular heat source outside the system and provides an advantageous e~ect of cooling the compressor to prevent overheating.
Furthermore, in the embodiment shown in Figure 7, since the coolant on -the lower temperature side o~ the vortex tube is cooled in the heat exchanger and then mixed with the coolant on the higher temperature side, the -temperature of the coolant entering the evaporator is lowered and, accordingly, the per~ormance can be improved when it is used as a re~rigerator or cooler.
__ __ _ __ __ Presæure(G) Tempera-kg/cm2ture ( C) Evaporator evaporation ¦ 0.9 -28 temperature .. .. .... _ _ Compressor suction side 0.9 5 discharge side13.2 97 _. . ..... _ .. . _ .
supply port13.2 95 exit for high13.2 131 Vortex tube temperature gas exit for low8.5 15 . ~ temperature gas _ _ __ ~ A ~Wf~
r , r j inlet Z 12.7 131 Condenser l , , ¦outlet 1 12.7 ' 36 _ __ _ _,_ _ _ _ . . ._._ l, ._.. . . _, ... , _~ ,. . .. . ....
Expansion inlet 1 12.7 ~ 5 valve loutlet ~ 0.9 1 -28 ~ L~
Further, water at 16 C supplied as the heat source (15 Q/min) to the e-vaporator 1 was cooled to water at 6 C, while water at 16 C supplied to -the condenser (30 Q/min) was warmed -to 74 C and then discharged.
Accordingly, the hea-t calorie emitted from the condenser was :
(74 -16) C x 30 Q x 60 min = 104,400 kcal/hour, and the heat calorie taken from the heat source was :
(16 - 6) C x 15 Q x 60 min = 9,000 kcal/hour Since -the heat calorie obtainable from the amount of work is : 7.5 kW x 860 kcal/hour = 6450 kcal/hour, and the rated input of the compressor used is 7.5 kW, the coeffi-cient of performance determined actually in the refrige-rating cycle of the present test example is represented based on the rated input of the compressor as :
- = ~ = 16.2 7.5 (kW) x 860 (kcal/hour) 6450 Industrial Applicability According to the reversed Rankine cycle apparatus of this lnvention, since the most portion of the superheated 737~
vapors of coolant rendered to high pressure and high tempera-ture in -the compressor is condensated after being raised to a higher tempera-ture by the vortex tube, the heat exchanging efficiency in the condenser can be improved to take out heat at higher -tempera-tureO
Specifically, the coefficient of performance h f the reversed ~ankine cycle apparatus according to this invention, when it is used as the heat pump cycle is determined based on the embodiment in Figure 4 as :
m(i3 - i6) m((i4 - i3) ~ (i6 - i5)) h + ~~ ~ ...(equation 1) i3 - i2 i3 - i2 (where m is a flow rate ratio flowing to the higher temperature side of the vortex tube, which ls smaller than 1). As compared with the coefficient of performance in the conventional heat pump cycle, it is increased by about ;
((i4 - i3) ~ (i6 - i5)) i3 - i2 in the case of m - 1. Accordingly, as already described above, since the operation is carried out, in the reversed Rankine cycle according to this invention, while setting the flow rate ratio for the coolant on the higher tempera-ture side at, preferably, from about 95 % to 9~ %, the coefficient of performance can be improved significantly.
In order to increase the entropy of -the coolant to -the same state as tha-t shown in ~igure 4 only by a compressor as in the usual case, the compressor has to ~Z473~
perform a great amount of work to result in problems in view of the heat durability and the eleckric power consumption thereo~, In addition, the p,i diagram take~
a vertically ex-tended configuration to provide a difficulty in the -throttling expansion failing to obtain desired coefficient of performance. ~hile on the other hand, according to this invention, no such problems are cau~ed since the enthalpy of the coolant discharged from the compressor is increased by the vortex tube. Further, since the coolant on the lower temperature side of the vortex tube can also get the energy in -the circuit 7 from the external atmosphere or from the heat source of the hea-t exchanger, a further contribution can be made to the improvement in the coefficient of performance. Further-more, since the relationship between the coefficient of performance ~h as the heat pump cycle and the coefficient o~ performance ~c as the refrigerator cycle is expressed as : ~c = ~h ~ 1, the improvement in the coefficient of performance of the heat pump cycle just means the improvement in the coef~icient of performance in the refrigerator cycle and, accordingly, this invention can improve the performance when it is used both to -the heat pump and to the refrigerator.
In the embodiment shown in Figure ~ and Figure 6, since the coolant on the lower temperature side of the vortex tube absorbs heat by means of the heat exchanger ~737~
and -then mixed with the coolant on -the higher temperature side, the enthalpy (i6 - i5) in the above mentioned equation 1 is increased and, accordingly, the coe~icienk o~ perfo:rmance when it is used as the heat pump can further be improved. Particularly, in the embodiment shown in Figure 6, ~ince the outer circumference of the compres~or ls used as the hea-t exchanglng section in the circuit 7 where the hea-t at the outer circumference o~ the compressor raised -to a higher temperature ls absorbed, it has a merit of requiring no particular heat source outside the system and provides an advantageous e~ect of cooling the compressor to prevent overheating.
Furthermore, in the embodiment shown in Figure 7, since the coolant on -the lower temperature side o~ the vortex tube is cooled in the heat exchanger and then mixed with the coolant on the higher temperature side, the -temperature of the coolant entering the evaporator is lowered and, accordingly, the per~ormance can be improved when it is used as a re~rigerator or cooler.
Claims (10)
1. A method of intensifying heat in a reversed Rankine cycle, which comprises:
- introducing superheated vapors of coolant at a high pressure discharged from a compressor in a reversed Rankine cycle to the supply port of a vortex tube, - separating the superheated vapors of coolant into higher and lower temperature components through energy separation such that from 70% to 100% of the introduced superheated vapors of coolant is discharged from an exit on the higher temperature side of said vortex tube and the remaining portion thereof discharged from an exit on the lower temperature side of said vortex tube, - condensating the superheated vapors of coolant raised to a higher temperature separated to the exit on the higher temperature side of the vortex tube by a condenser in the reversed Rankine cycle, and - recycling the vapors of coolant rendered to a lower temperature separated to the exit on the lower temperature side of the vortex tube to the system of the reversed Rankine cycle.
- introducing superheated vapors of coolant at a high pressure discharged from a compressor in a reversed Rankine cycle to the supply port of a vortex tube, - separating the superheated vapors of coolant into higher and lower temperature components through energy separation such that from 70% to 100% of the introduced superheated vapors of coolant is discharged from an exit on the higher temperature side of said vortex tube and the remaining portion thereof discharged from an exit on the lower temperature side of said vortex tube, - condensating the superheated vapors of coolant raised to a higher temperature separated to the exit on the higher temperature side of the vortex tube by a condenser in the reversed Rankine cycle, and - recycling the vapors of coolant rendered to a lower temperature separated to the exit on the lower temperature side of the vortex tube to the system of the reversed Rankine cycle.
2. The method of intensifying heat as defined in claim 1, wherein from 95% to 98% of the superheated vapors of coolant at a high pressure introduced into the vortex tube is discharged from the exit on the higher temperature side and the remaining portion thereof is discharged from the exit on the lower temperature side thereby separating the superheated vapors of coolant into higher and lower temperature components through energy separation.
3. The method of intensifying heat as defined in claim 1, wherein heat is supplied to the coolant from the exit on the lower temperature side of the vortex tube and then it is recycled to the system of the reversed Rankine cycle.
4. The method of intensifying heat as defined in claim 2, wherein heat is supplied to the coolant from the exit on the lower temperature side of the vortex tube and then it is recycled to the system of the reversed Rankine cycle.
5. The method of intensifying heat as defined in claim 3, wherein the heat of the compressor is supplied to the coolant separated to the exit on the lower temperature side of the vortex tube.
6. The method of intensifying heat as defined in claim 1 or 2, wherein a portion of the heat of the coolant separated to the exit on the lower temperature side of the vortex tube is absorbed.
7. A reversed Rankine cycle apparatus wherein coolant is recycled as an operational fluid, comprising:
- at least one vortex tube in which from 70% to 100% of a gas introduced at a high pressure is discharged from an exit on the higher temperature side of the vortex tube and the remaining portion is discharged from an exit on the lower temperature side of the vortex tube to thereby separate said introduced gas into higher and lower temperature components through energy separation, wherein:
a coolant circuit on the discharging side of a first compressor in the reversed Rankine cycle is connected to a supply port for pressurized gas of the vortex tube, a coolant circuit on the higher temperature side of a second condenser in the reversed Rankine cycle is connected to the exit on the higher temperature side of the vortex tube, and the exit on the lower temperature side of the vortex tube is connected with the coolant circuit on the lower temperature side of said second condenser by means of a circuit.
- at least one vortex tube in which from 70% to 100% of a gas introduced at a high pressure is discharged from an exit on the higher temperature side of the vortex tube and the remaining portion is discharged from an exit on the lower temperature side of the vortex tube to thereby separate said introduced gas into higher and lower temperature components through energy separation, wherein:
a coolant circuit on the discharging side of a first compressor in the reversed Rankine cycle is connected to a supply port for pressurized gas of the vortex tube, a coolant circuit on the higher temperature side of a second condenser in the reversed Rankine cycle is connected to the exit on the higher temperature side of the vortex tube, and the exit on the lower temperature side of the vortex tube is connected with the coolant circuit on the lower temperature side of said second condenser by means of a circuit.
8. The reversed Rankine cycle apparatus as defined in claim 7, wherein the flow rate ratio at the exit on the higher temperature side of the vortex tube is set at from 95% to 98%.
9. The reversed Rankine cycle apparatus as defined in claim 7, wherein the circuit connecting the exit on the lower temperature side of the vortex tube with the coolant circuit on the lower temperature side of the second condenser has a heat exchanger for supplying heat to the coolant in said circuit or absorbing the heat from said coolant.
10. The reversed Rankine cycle apparatus as defined in claim 9, wherein the heat exchanger of the circuit is disposed at the outer circumference of the first compressor, by which the heat from the first compressor is caused to be absorbed into the coolant in the circuit.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP78699/1984 | 1984-04-20 | ||
| JP7869984A JPS60223969A (en) | 1984-04-20 | 1984-04-20 | Refrigeration cycle device |
| JP10966284A JPS60253768A (en) | 1984-05-31 | 1984-05-31 | Reverse rankine cycle device in which vortex tube is combined |
| JP109662/1984 | 1984-05-31 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1247376A true CA1247376A (en) | 1988-12-28 |
Family
ID=26419754
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000479599A Expired CA1247376A (en) | 1984-04-20 | 1985-04-19 | Method of intensifying heat in reversed rankine cycle and reversed rankine apparatus for conducting the same |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1247376A (en) |
-
1985
- 1985-04-19 CA CA000479599A patent/CA1247376A/en not_active Expired
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