CN1683842A - Steam compression type refrigeration cycle device of approximate ideal inverse Carnot cycle efficiency - Google Patents
Steam compression type refrigeration cycle device of approximate ideal inverse Carnot cycle efficiency Download PDFInfo
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Abstract
The steam compressing refrigeration cycle device includes main cycle system comprising booster pump, condensator, expansion motor, evaporator and compressor connected successively with pipeline to output cold; and secondary cycle system comprising throttle connected across the inlet of the booster pump and the outlet of the condensator as well as the booster pump and the condensator, to further lower the temperature of the work medium in the outlet of the compressor. The expansion motor has its output torque rotating the booster pump and has isoentropic expansion to reduce the entropy of the work medium entering the condensator. The booster pump reduces the operation pressure difference and the power consumption of the compressor. Therefore, the present invention has energy efficiency near ideal inverse Carnot cycle and low hot load one compressor, and may be used widely in refrigeration cycle in air conditioner, refrigerator, etc.
Description
Technical field
The present invention relates to a kind of refrigerating plant, particularly relate to a kind of steam compression type refrigeration cycle device.Be applicable to refrigeration technology fields such as air-conditioning, refrigerator.
Background technology
Traditional steam compressed refrigerating circulating system such as Fig. 1 in order to reach the refrigeration purpose, adopt compressor 1 adiabatic isentropic Compression more, condenser 2 isobaric condensation heat releases, flow controller 3 isenthalpic throttling step-downs cooling, the thermodynamic cycle process of evaporimeter 4 isobaric heat absorptions refrigeration.The outlet of evaporimeter 4 is connected with the import of compressor 1 among the figure; The outlet of compressor 1 is connected with the import of condenser 2; The outlet of condenser 2 is connected with the import of flow controller 3; The outlet of flow controller 3 is connected with the import of evaporimeter 4.
Pressure-enthalpy chart such as Fig. 3 of traditional steam compression type refrigerating circulation, P is the pressure of working medium, H is the enthalpy of working medium; Tephigram such as Fig. 4.T is the temperature of working medium, and S is the entropy of working medium.Can see among the figure: 7 → 15 processes enter compressor 1 adiabatic isentropic Compression for the low pressure working fluid behind evaporimeter 4 absorption refrigerations, heat the thermal procession that supercharging increases enthalpy; 15 → 17 → 11 processes are the HTHP working medium after compressed machine 1 compression, enter the isobaric cooling of condenser 2 leading portions cooling heat dissipation, the thermal procession of the isobaric isothermal condensation of back segment heat release; 11 → 14 processes enter flow controller 3 isenthalpic throttlings and expand for to force down enthalpy working medium through condenser 2 condensed height, and the step-down cooling increases the thermal procession of entropy; 14 → 7 processes are the low-temp low-pressure working medium through flow controller 3 throttlings, the thermal procession that enters evaporimeter 4 isothermal and isobaric absorption refrigerations.
" refrigeration principle and equipment " the 5th page of introduction that publishing house of Xi'an Communications University published in 1997, this thermodynamic cycle process American PerkiNs in 1834 has obtained patent No. 6662 in Britain.Traditional steam compressed refrigerating circulating system is owing to the equipment maturation, so until still obtain a large amount of uses at present.
In the hot merit theory, desirable kind of refrigeration cycle is contrary Carnot cycle.This circulation is made up of two constant temperature process and two adiabatic process.Its pressure-enthalpy chart such as Fig. 5, P are the pressure of working medium, and H is the enthalpy of working medium; The contrary Carnot cycle tephigram of imaginary steam refrigerating such as Fig. 6, T is the temperature of working medium, S is the entropy of working medium.Can see among the figure that 7 → 16 processes are the adiabatic isentropic Compression of refrigeration working medium, heat the thermal procession that supercharging increases enthalpy; 16 → 17 → 11 processes are the thermal procession of refrigeration working medium isothermal supercharging (this violates the hot merit theory, can not realize) and isothermal and isobaric condensation heat release; 11 → 13 processes are the adiabatic constant entropy expansion of refrigeration working medium, and the thermal procession of enthalpy falls in step-down; 13 → 7 processes are the thermal procession of refrigeration working medium isothermal and isobaric absorption refrigeration.
The kind of refrigeration cycle process of above-mentioned traditional steam compressed refrigerating circulating system is compared with the ideal inverse carnot's cycle process, exists steam and crosses hot press method and isenthalpic throttling process.See among Fig. 7 and Fig. 8 16 → 15 processes, the thermal procession that compressor 1 adiabatic constant entropy is crossed hot compression; 11 → 14 processes, the thermal procession of the isenthalpic throttling step-down cooling of flow controller 3.The refrigeration efficiency of this kind of refrigeration cycle is much smaller than the efficiency of desirable contrary Carnot cycle.And traditional steam compressed refrigerating circulating system makes that also the working heat load of compressor is too high.It is low more particularly to work as cryogenic temperature, and its refrigeration efficiency is big more less than the difference of the contrary Carnot cycle efficiency of hot merit theory.The thermodynamics sophistication of general air-conditioning has only 70%, and refrigerator has only 40%.
Summary of the invention
Low in order to solve traditional steam compressed refrigerating circulating system circulation efficiency, problem such as the thermic load of compressor is big the invention provides a kind of steam compression type refrigeration cycle device of approximate ideal inverse Carnot's cycle efficiency.This system can improve the efficiency of Vapor Compression Refrigeration Cycle significantly and reduce the working heat load of compressor significantly.
Characteristics of the present invention are, behind the condenser condenses exothermic process of the steam compression type refrigeration circulatory system, obtained most of refrigeration working medium of condensation, by being connected the expansion motor of condensator outlet, carry out constant entropy expansion acting step-down and fall enthalpy, produce the working medium of the low enthalpy of low-temp low-pressure, be input to evaporator inlet, be used for the isobaric heat absorption refrigeration; Obtain the fraction refrigeration working medium of condensation, by also being connected the flow controller of condensator outlet, isenthalpic throttling step-down cooling produces the working medium of medium temperature and medium pressure, after compressor outlet mixes through the middle pressure working medium equipressure of compressor isentropic Compression, enters the adiabatic constant entropy supercharging of booster pump again.Through the high enthalpy working medium of HTHP of booster pump supercharging, enter the isobaric condensation heat release of condenser.
The steam compression type refrigeration cycle device of approximate ideal inverse Carnot's cycle efficiency of the present invention comprises: compressor, condenser, flow controller and evaporimeter; The present invention is different from the prior art part and is: also comprise being used to reduce expansion motor that enters described condenser working medium enthalpy and the booster pump that is used to reduce described compressor operating pressure; Described booster pump, condenser, expansion motor, evaporimeter, compressor are communicated with the formation major circulatory system successively by pipeline, this major circulatory system output cold; The described flow controller of cross-over connection between the exit of the porch of the booster pump of described major circulatory system and condenser, formation is from booster pump, condenser, pass through flow controller again, return the inferior circulatory system of booster pump, this time circulatory system reduces the working medium temperature after the described compressor compresses, and enthalpy reduces.
The output torque that produces when described expansion motor expands is used for driving booster pump work.Working medium after the described flow controller throttling, the working medium after compressor compresses carry out entering after equipressure is mixed the adiabatic supercharging of described booster pump; The outlet pressure of described expansion motor is lower than the outlet pressure of flow controller; The flow of described expansion motor is greater than the flow of flow controller.And the flow of booster pump is greater than the flow of compressor; The flow of condenser is greater than the flow of described evaporimeter.
Compare with traditional steam compressed refrigerating circulating system, cooling cycle system of the present invention has following beneficial effect:
1. refrigeration efficiency obviously improves.
2. a compressor row mouthful working medium temperature obviously reduces.
3. big more with the kind of refrigeration cycle working medium temperature difference, the efficiency that is improved is also big more, and its thermodynamic perfect degree changes very little.
Description of drawings
Fig. 1 is traditional steam compressed refrigerating circulating system figure;
Fig. 2 is the steam compressed refrigerating circulating system figure of approximate ideal inverse Carnot's cycle efficiency of the present invention;
Fig. 3 is the pressure-enthalpy chart of traditional steam compression type refrigerating cyclic process;
Fig. 4 is the tephigram of traditional steam compression type refrigerating cyclic process;
Fig. 5 is the pressure-enthalpy chart of desirable contrary Kano steam refrigerating cyclic process;
Fig. 6 is the tephigram of desirable contrary Kano steam refrigerating cyclic process;
Fig. 7 is traditional steam refrigerating circulation and contrary Kano steam refrigerating recycle ratio pressure-enthalpy chart;
Fig. 8 is traditional steam refrigerating circulation and contrary Kano steam refrigerating recycle ratio tephigram;
Fig. 9 is the pressure-enthalpy chart of approximate ideal inverse Carnot cycle of the present invention;
Figure 10 is the tephigram of approximate ideal inverse Carnot cycle of the present invention;
Figure 11 is steam refrigerating circulation of the present invention and traditional steam refrigerating circulation and desirable contrary Kano steam refrigerating recycle ratio pressure-enthalpy chart;
Figure 12 is steam refrigerating circulation of the present invention and traditional steam refrigerating circulation and desirable contrary Kano steam refrigerating recycle ratio tephigram;
Figure 13 is the system diagram of the steam refrigerating EGR embodiment of approximate ideal inverse Carnot's cycle efficiency of the present invention;
Figure 14 implements the system diagram that traditional steam refrigerating circulates for using the water-cooled compressor for cold water group in the accompanying drawing 13.
The specific embodiment
Steam compression type refrigeration cycle device of the present invention as shown in Figure 2, the outlet of compressor 22 is connected to the import of booster pump 24 with after the outlet of flow controller 25 is in parallel.After the inlet parallel of the import of expansion motor 26 and flow controller 25, be connected to the outlet of condenser 23.The import of evaporimeter 27 is connected with the outlet of expansion motor 26, and the outlet of evaporimeter 27 is connected with the import of compressor 22.The outlet of booster pump 24 is connected with the import of condenser 23. Expansion motor 26 and 24 coaxial connections of booster pump.
In kind of refrigeration cycle of the present invention, the constant entropy expansion effect of expansion motor 26 makes the enthalpy that enters condenser working medium significantly reduce; The use of booster pump 24 makes the operting differential pressure of compressor 22 diminish, and required energy consumption reduces; The working medium of the isenthalpic throttling of flow controller 25 reduces the working medium temperature in described compressor 22 exits in the inferior circulatory system.So the present invention has the efficiency of approximate inverse Kano kind of refrigeration cycle and lower compressor heat load.
Pressure-enthalpy chart such as Fig. 9 of steam compression type refrigerating circulation of the present invention, P is the pressure of working medium, H is the enthalpy of working medium; Tephigram such as Figure 10.T is the temperature of working medium, and S is the entropy of working medium.Described major circulatory system is the direction by 7 → 8 → 9 → 10 → 11 → 13 → 7, realizes the circulation of most of refrigeration working medium.Described the circulatory system is the direction by 9 → 10 → 11 → 12 → 9, realizes the circulation of fraction refrigeration working medium.
From Fig. 9, Figure 10, can see following process:
A.7 → 8 process is the low pressure working fluid behind the evaporimeter absorption refrigeration, enters compressor constant entropy adiabatic compression, heats the thermal procession that supercharging increases enthalpy;
B.8 → 9 process is the middle pressure working medium after the compression of compressed machine, and mixes from the medium temperature and medium pressure working medium after the flow controller throttling is isobaric, falls the thermal procession of enthalpy;
C.9 → 10 process is the working medium of mixing through equipressure, enters the thermal procession of the adiabatic supercharging of booster pump;
D.10 → 17 → 11 process is the HTHP working medium after the booster pump supercharging, enters the isobaric cooling of condenser leading portion cooling heat dissipation, the thermal procession of the isobaric isothermal condensation of back segment heat release;
E.11 → 13 process is the most of high-pressure working medium after condenser condenses, enters the adiabatic constant entropy expansion of expansion motor, and the thermal procession of enthalpy falls in step-down;
F.13 → 7 process is the low enthalpy working medium of low-temp low-pressure after the expansion of expansion motor, enters the thermal procession of evaporimeter isobaric heat absorption refrigeration;
G.11 → 12 process is the fraction high-pressure working medium after the condenser condenses heat release, enters the thermal procession that flow controller isenthalpic throttling expansion step-down cooling increases entropy;
H.12 → 9 process is the medium temperature and medium pressure working medium after the flow controller throttling, and mixes from the middle pressure working medium after the compressor compresses is isobaric, and isothermal increases the thermal procession of enthalpy.
From Figure 11 and Figure 12, can be clearly seen that:
1. the thermal procession 11 → 13 of enthalpy falls in the adiabatic constant entropy expansion of the expansion motor in the kind of refrigeration cycle of the present invention, step-down, and the flow controller isenthalpic throttling that has substituted in traditional kind of refrigeration cycle expands, and the step-down cooling increases the thermal procession 11 → 14 of entropy.With the adiabatic constant entropy expansion of the refrigeration working medium in the desirable contrary Carnot cycle, the thermal procession that enthalpy falls in step-down coincides.The enthalpy of the refrigeration working medium that enters evaporimeter is obviously reduced, and the efficiency of evaporimeter isobaric heat absorption refrigeration significantly improves.
2. the compressor constant entropy adiabatic compression in the kind of refrigeration cycle of the present invention, heat supercharging and increase the thermal procession 7 → 8 of enthalpy,, heat the thermal procession 7 → 15 that supercharging increases enthalpy and compare with the adiabatic isentropic Compression of the compressor in traditional kind of refrigeration cycle, process obviously shortens, and the energy consumption of compressor significantly reduces.
3. the steam in traditional kind of refrigeration cycle is crossed hot press method 8 → 15, is cancelled in kind of refrigeration cycle of the present invention.The working heat load of compressor obviously reduces, and pressure load also significantly reduces.
4. the thermal procession 15 → 17 of the isobaric cooling of the condenser leading portion in traditional kind of refrigeration cycle cooling heat dissipation shortens to the thermal procession 10 → 17 of the isobaric cooling of the condenser leading portion cooling heat dissipation in the kind of refrigeration cycle of the present invention.The temperature and the enthalpy that enter the superheated vapor of condenser all obviously reduce, and the load of condenser condenses heat release can significantly reduce.
5. the thermodynamics sophistication in the circulation of traditional steam refrigerating is along with the temperature difference increase of condensation temperature and evaporating temperature and reduce.And the thermodynamics sophistication in the steam refrigerating circulation of the present invention is almost constant when the temperature difference of condensation temperature and evaporating temperature changes.Help like this when cooling condition changes, efficiently moving always.
As Fig. 9, shown in Figure 10: when in system, being filled with cold-producing medium working medium, give compressor 22 input powers, this working medium with 1-m amount from state 7 by compressor 22 adiabatic compression to superheated vapor state 8, measure working medium with the m that has through flow controller 25 isenthalpic throttling step-downs cooling, equipressure is mixed into damp steam state 9, and be pressurized to superheated vapor state 10 through booster pump 24 thermal insulation, the working medium flow unit of being defined as 1 of this supercharging thermal procession enters condenser 23 subsequently and carries out the wet saturated liquid working medium 11 of isobaric condensation heat release formation high pressure.Then this working medium is divided into two the tunnel, has a road of 1-m amount and enters expansion motor 26 adiabatic expansions and enter evaporimeter 23 to damp steam attitude 13, gets back to the compressor inlet of state 7 and finish kind of refrigeration cycle one time after equipressure is evaporated absorption refrigeration.This circulation claims that for the closed process part of 7 → 8 → 9 → 10 → 11 → 13 → 7 among the figure this circulation is major cycle.Another road with m amount enters flow controller 25 isenthalpic throttling step-downs and cools to state 12, there is the working medium equipressure of 1-m amount to be mixed into damp steam attitude 9 with the middle pressing element of compressed machine 22 compressions, enter booster pump 24 adiabatic superchargings again, realize one time auxiliary circulation, this circulation is the closed process part of 9 → 10 → 11 → 12 → 9 among the figure, claims this circulation to be time circulation.Inferior circulation can make the working medium temperature T 8 of compressor 22 outlets drop to T9, and booster pump 24 reduces the operating pressure of compressor 22 in the major cycle, and power consumption reduces.Have a road of 1-m amount and enter mechanical power that expansion motor 26 adiabatic expansions send to damp steam attitude 13 and be imported into booster pump 24 and be used for the supercharging wasted work, it is compound that primary and secondary circulates is kind of refrigeration cycle of the present invention.
Its circulation efficiency ξ e theoretical value is: ξ e==(ξ z+E)/(1-E) (18)
Inferior cycle fluid flow m theoretical value is: m==1/ ξ c (ξ k+D) (19)
(18) in the formula,
ξ z is the theoretical efficiency (being traditional circulation efficiency) of PerkiNs steam refrigerating circulation 7 → 15 → 11 → 14 → 7;
E is the ratio of the enthalpy difference of the relative recurrent state point 15,7 of the enthalpy difference of recurrent state point 14,13.
(19) in the formula,
ξ k is the theoretical efficiency (both Carnot cycle efficiencies) of desirable Lao Lunzi steam refrigerating circulation 8-15-10-9-8;
ξ c is the theoretical efficiency (both time circulation efficiencies) of PerkiNs steam refrigerating circulation 9 → 10 → 11 → 12 → 9;
D is the ratio of the enthalpy difference of the relative recurrent state point 8,9 of the enthalpy difference of recurrent state point 10,9.
Since E concerning with cold-producing medium working medium with gas-liquid binary states greater than zero, and increase with the difference of circulating pressure P11 and P7.The theoretical maximum of ξ e is the Kano efficiency ξ k of steam refrigerating circulation 7 → 15 → 11 → 13 → 7.Its size is by the ξ z size and the decision of E value size of reality.
Table 1 is a cycle fluid when being R22, the kind of refrigeration cycle of two kinds of different operating modes, the theoretical computational chart of ξ Ko, ξ z, ξ e.T16, T15, T8 are according to R22 performance parameter calculated value.ξ Ko is the efficiency of ideal inverse Kano kind of refrigeration cycle, and ξ z is the efficiency that traditional steam refrigerating circulates, and ξ e is the efficiency of approximate ideal inverse Carnot cycle of the present invention.M is the percent value of time relative condenser 23 working medium flows of cycle fluid flow.T11 is a condensation temperature, and T7 is an evaporating temperature.T16, T15, T8 are respectively the temperature of the corresponding operating point of circulation.
Table 1 (working medium R22)
| State of cyclic operation | ????????ξKo | ????ξz | ????ξe | ??T16 | ??T15 | ??T8 | ??m | ||
| ???T11 | ???T7 | η thermodynamics sophistication | |||||||
| ??40℃ | ???2℃ | ????ξ | ???7.24 | ???5.94 | ???7.09 | ??40℃ | ??73℃ | ??40.1℃ | ??0.05 |
| ????η | ???1 | ???0.82 | ???0.98 | ||||||
| ??40℃ | ???-20℃ | ????ξ | ???4.22 | ???3.15 | ???4.21 | ??40℃ | ??73℃ | ??40.1℃ | ??0.04 |
| ????η | ???1 | ???0.74 | ???0.99 | ||||||
The result of calculation of ξ Ko from table 1, ξ z, ξ e and T16, T15, T8 can see that ξ e value is in ξ Ko between ξ z value, and near ξ Ko.The T8 value at T16 between the T15 value, and near T16.
Accompanying drawing 13 is embodiments of the invention, and promptly cold is 23KW water-cooled water chilling unit system figure.
Comprise among the figure: the revolution discharge capacity is 0.11 liter, and motor rated power is 5 kilowatts a compressor bank 32; Heat exchange area is 4.5 square metres a tubular water condenser ' 33; Manufacture and design according to the quadric chain principle, the revolution discharge capacity is 0.1 liter piston type booster pump 34; The throttle orifice sectional area that has check valve is 6 square millimeters an one-way throttle device 35, and the use of check valve is for convenience of loop start; Manufacture and design according to the quadric chain principle, power revolution discharge capacity is 0.02 liter a piston type expansion motor 36 without acceptance of persons; Heat exchange area is 4.5 square metres a horizontal cold water evaporimeter 37, by cold water output cold; Volume is 60 liters a reservoir 38.Wherein expansion motor 36 and booster pump 34 are the new-type element in steam compression type refrigerating circulating technology field.
Comprise also in the system that refrigeration working medium fills, the discharging interface, and heat exhaust is 27 kilowatts forced ventilation blowing-type cooling tower, do not draw among the figure.
As shown in figure 13, the outlet of described compressor 32 is connected to the import of booster pump 34 with after the outlet of one-way throttle device 35 is in parallel.The import of the import of expansion motor 36 and one-way throttle device 35 by reservoir 38 in parallel after, be connected to the outlet of condenser 33.The import of evaporimeter 37 is connected with the outlet of expansion motor 36, and the outlet of evaporimeter 37 is connected with the import of compressor 32.The outlet of booster pump 34 is connected with the import of condenser 33. Expansion motor 36 and 34 coaxial connections of booster pump make booster pump 34 reclaim the kinetic energy that is produced when expansion motor 36 expands.
Table 2 is this embodiment approximate ideal inverse Kano steam refrigerating circulatory system measurement data measure and calculate table.
In device, be filled with R22 cold-producing medium working medium, when the pressure reduction that advances row mouthful when compressor reaches 10bar, stop to fill cold-producing medium.System's continous-stable moves measurement data two days later.
Table 2 (working medium R22)
| ??T11 | ??T7 | ??T8 | ??T10 | ????W | ????Q | ???ξe | ?????ηe |
| ??40.3℃ | ??1.6℃ | ??40.5℃ | ??48℃ | ????4.68 | ????23.2 | ???4.96 | ?????0.685 |
| ??8℃ | ??40.3℃ | ??47.5℃ | ????3.8 | ????22.8 | ???6 | ?????0.696 |
In the table 2, W is the input power of system, and Q is the output cold of system, and ξ e is the circulation efficiency, and η e is the thermodynamics sophistication.T11 is a condensation temperature, and T7 is an evaporating temperature.T8 is the outlet temperature of compressor 32, the outlet temperature of T10 booster pump 34.
Accompanying drawing 14 is to use the water-cooled compressor for cold water group in the accompanying drawing 13 to implement the system diagram of traditional steam refrigerating circulation.
Differently in the system be that having used throttle diameter is 10 millimeters outer balanced type heating power expansion valve 39, has replaced piston type expansion motor 36; And piston type booster pump 34 and one-way throttle device 35 have been cancelled.
Table 3 is that this system is traditional steam refrigerating circulatory system measurement data measure and calculate table.
Table 3 (working medium R22)
| ??T11 | ????T7 | ??T15 | ????W | ????Q | ????ξz | ?????ηz |
| ??40℃ | ????1.6℃ | ??69.5℃ | ????4.83 | ????20.1 | ????5.16 | ?????0.576 |
| ????8℃ | ??68.2℃ | ????3.74 | ????19.3 | ????4.16 | ?????0.586 |
In the table 3, W is the input power of system, and Q is the output cold of system, and ξ z is the circulation efficiency, and η z is the thermodynamics sophistication.T11 is a condensation temperature, and T7 is an evaporating temperature.T15 is the outlet temperature of compressor 32.
The circulation efficiency in table 2 table 3 and the gap of thermodynamics sophistication and table 1 are that mechanical friction loss and power loss produce owing to have thermodynamic loss in the system.Can find out that by theoretical computational chart 1 of data and measure and calculate table 2. tables 3 steam refrigerating circulation in approximate ideal inverse Kano has refrigeration efficiency and obviously improves; A compressor row mouthful working medium temperature obviously reduces; T11-T13 is big more with the kind of refrigeration cycle working medium temperature difference, and the efficiency that is improved is also big more, and its thermodynamic perfect degree changes advantages such as very little.
Claims (7)
1. the steam compression type refrigeration cycle device of an approximate ideal inverse Carnot's cycle efficiency comprises: compressor (22), condenser (23), flow controller (25) and evaporimeter (27); Its special seized with terror being:
Also comprise and be used for reducing the booster pump (24) that enters the expansion motor (26) of described condenser (23) working medium enthalpy and be used to reduce described compressor (22) operating pressure;
Described booster pump (24), condenser (23), expansion motor (26), evaporimeter (27), compressor (22) are communicated with the formation major circulatory system successively by pipeline, this major circulatory system output cold;
The described flow controller of cross-over connection (25) between the exit of the porch of the booster pump (24) of described major circulatory system and condenser (23), formation is from booster pump (24), condenser (23), pass through flow controller (25) again, return the inferior circulatory system of booster pump (24), this time circulatory system reduces the working medium temperature after described compressor (22) compression, and enthalpy reduces.
2. as claim 1 described refrigerating circulatory device, its special seized with terror being: the output torque of described expansion motor (26) drives described booster pump (24).
3. as claim 1 described refrigerating circulatory device, its special seized with terror being: the working medium after described flow controller (25) throttling is mixed with the working medium equipressure after described compressor (22) compression, enters the adiabatic supercharging of described booster pump (24) together.
4. as claim 1 or 2 described refrigerating circulatory devices, its special seized with terror being: the outlet pressure of described expansion motor (26) is lower than the outlet pressure of flow controller (25).
5. as claim 1 or 2 described refrigerating circulatory devices, its special seized with terror being: the working medium flow of described expansion motor (26) is greater than the working medium flow of described flow controller (25).
6. as claim 1 or 2 described refrigerating circulatory devices, its special seized with terror being: the working medium flow of described booster pump (24) is greater than the working medium flow of described compressor (22).
7. as claim 1 described refrigerating circulatory device, its special seized with terror being: the working medium flow of described condenser (23) is greater than the working medium flow of described evaporimeter (27).
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| ES2134580T3 (en) * | 1995-02-06 | 1999-10-01 | Carrier Corp | LOGICAL-INDEFINITE CONTROL OF LIQUID INJECTION TO COOL THE ENGINE. |
| JPH10153352A (en) * | 1996-11-21 | 1998-06-09 | Kobe Steel Ltd | Refrigerating device |
| US6584784B2 (en) * | 1999-02-05 | 2003-07-01 | Midwest Research Institute | Combined refrigeration system with a liquid pre-cooling heat exchanger |
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