CN103743150A - Absorption compression type automatic-overlapping refrigerating system and use method - Google Patents

Absorption compression type automatic-overlapping refrigerating system and use method Download PDF

Info

Publication number
CN103743150A
CN103743150A CN201310695791.XA CN201310695791A CN103743150A CN 103743150 A CN103743150 A CN 103743150A CN 201310695791 A CN201310695791 A CN 201310695791A CN 103743150 A CN103743150 A CN 103743150A
Authority
CN
China
Prior art keywords
gas
liquid
phase working
needed
heat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN201310695791.XA
Other languages
Chinese (zh)
Other versions
CN103743150B (en
Inventor
王厉
骆菁菁
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Chongqing Kuizhou Cold Chain Logistics Co.,Ltd.
Original Assignee
Zhejiang Sci Tech University ZSTU
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zhejiang Sci Tech University ZSTU filed Critical Zhejiang Sci Tech University ZSTU
Priority to CN201310695791.XA priority Critical patent/CN103743150B/en
Publication of CN103743150A publication Critical patent/CN103743150A/en
Application granted granted Critical
Publication of CN103743150B publication Critical patent/CN103743150B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Abstract

The invention discloses an absorption compression type automatic-overlapping refrigerating system and a use method. The absorption compression type automatic-overlapping refrigerating system comprises a generator and the like; the generator is communicated with a solution heat exchanger which is communicated with an absorber; the absorber is further communicated with the solution heat exchanger which is communicated with the generator; the generator is communicated with a condenser which is communicated with a gas-liquid separator; the gas-liquid separator is further communicated with an evaporative condenser which is communicated with a first gas-liquid heat exchanger, the first gas-liquid heat exchanger is communicated with an evaporator which is communicated with the first gas-liquid heat exchanger, and the first gas-liquid heat exchanger is communicated with the evaporator which is communicated with the first gas-liquid heat exchanger communicated with a compressor; the gas-liquid separator is communicated with the evaporative condenser; the compressor and the evaporative condenser are communicated with the absorber.

Description

Absorb compression auto-cascading refrigeration system and using method
Technical field
The present invention relates to a kind of Refrigeration & Air-Conditioning equipment technical field, specifically a kind of compression auto-cascading refrigeration system and using method of absorbing.
Background technology
Auto-cascading refrigeration system adopts the different mixed working fluid of boiling point, by multi-stage gas-liquid, separate, rely on and separate intercoupling of the evaporation endothermic of the higher boiling component more than needed obtaining and the condensation heat release of low boiling component more than needed, can obtain lower refrigeration evaporator temperature, the temperature-changing characteristic that mixed working fluid has simultaneously can reduce the irreversible loss of evaporimeter.The evaporating temperature of auto-cascading refrigeration system is less than common refrigeration system to the dependence of pressure, and therefore the pressure ratio of its restriction loss and compressor is also less, conventionally with a compressor, just can meet application requirements.In order to utilize low-grade heat source (<200 ℃) acting, auto-cascading refrigeration system also can adopt absorption system to replace compressor, publication number be the patent documentation of CN102759218 disclose a kind of compress absorbing coupling from overlapping low-temperature refrigerator, the main feature of this refrigeration machine be higher boiling working medium more than needed in depress and absorb from low boiling working medium more than needed condensation heat under high pressure, low boiling working medium more than needed is under low pressure evaporated, and arrive high pressure by compressor compresses, mix and condensation with the higher boiling working medium more than needed from generator gaseous state out again.This system can obtain lower evaporating temperature in the situation that adopting single-stage fractional condensation, and still, in this system, low boiling working medium circulation more than needed is larger to the degree of dependence of compressor work, therefore can not utilize more low-grade heat source.Application number is that 200910304102.1 patent discloses a kind of pressure-boosting absorptive-type auto-cascade absorption refrigeration circulating system, the main feature of this system is to utilize from gas-liquid separator highly pressurised liquid out to enter the low-pressure steam out from evaporimeter of injection in injector, thereby low-pressure steam is played to certain pressurization, but injector be an irreversible loss compared with large equipment, larger on the impact of system effectiveness.
For this reason, need to provide one to there is greater efficiency, retain the flexibility of compressor boost, reduce the dependence to compressor work, can also improve the absorption compression auto-cascading refrigeration system of low-grade energy utilization rate.
Summary of the invention
The technical problem to be solved in the present invention is to provide a kind of absorption compression auto-cascading refrigeration system and using method simple in structure.
In order to solve the problems of the technologies described above, the invention provides a kind of compression auto-cascading refrigeration system that absorbs, comprise generator, solution heat exchanger, absorber, solution pump, condenser, gas-liquid separator, evaporative condenser, the first gas-liquid heat-exchange, evaporimeter and compressor, one end of the pyrosol pipeline of the taphole of described generator and solution heat exchanger is interconnected, and other one end of the pyrosol pipeline of solution heat exchanger and the solution inlet port of absorber are interconnected, one end of the cryogenic fluid pipeline of the taphole of described absorber and solution heat exchanger is interconnected, and other one end of the cryogenic fluid pipeline of described solution heat exchanger and the solution inlet port of generator are interconnected, one end of the gas vent of described generator and the condensation pipe of condenser is interconnected, and other one end of the condensation pipe of described condenser and the moist steam import of gas-liquid separator are interconnected, one end of the high temperature refrigerant pipeline of the gas vent of described gas-liquid separator and evaporative condenser is interconnected, one end of other one end of the high temperature refrigerant pipeline of evaporative condenser and the high-temp liquid pipeline of the first gas-liquid heat-exchange is interconnected, one end of other one end of the high-temp liquid pipeline of described the first gas-liquid heat-exchange and the evaporation tubes of evaporimeter is interconnected, one end of other one end of the evaporation tubes of evaporimeter and the cryogenic gas pipeline of the first gas-liquid heat-exchange is interconnected, other one end of the cryogenic gas pipeline of the first gas-liquid heat-exchange and the gas access of compressor are interconnected, one end of the taphole of described gas-liquid separator and the evaporation tubes of evaporative condenser is interconnected, other one end of the gas vent of described compressor and the evaporation tubes of evaporative condenser is interconnected with the gas feed of absorber respectively.
As the improvement of absorption compression auto-cascading refrigeration system of the present invention: be provided with first throttle valve between the pyrosol pipe end of described solution heat exchanger and the solution inlet port of absorber; Between the cryogenic fluid pipe end of the taphole of described absorber and solution heat exchanger, be provided with solution pump; Between the port of other one end of the high-temp liquid pipeline of described the first gas-liquid heat-exchange and the evaporation tubes of evaporimeter, be provided with the 3rd choke valve; Between the port of the taphole of described gas-liquid separator and the evaporation tubes of evaporative condenser, be provided with the second choke valve.
As the further improvement of absorption compression auto-cascading refrigeration system of the present invention: be connected with two-port valve between the gas feed of described compressor and the gas vent of compressor.
As the further improvement of absorption compression auto-cascading refrigeration system of the present invention: be provided with the second gas-liquid heat-exchange between described generator, solution heat exchanger and condenser; The cryogenic fluid pipeline of described solution heat exchanger and the low-temperature liquid pipe of the second gas-liquid heat-exchange interconnect, and the low-temperature liquid pipe of described the second gas-liquid heat-exchange is connected with the solution inlet port of generator; The gas vent of generator is connected with the hot-gas channel of the second gas-liquid heat-exchange, and the hot-gas channel of described the second gas-liquid heat-exchange and the condensation pipe of condenser interconnect.
As the further improvement of absorption compression auto-cascading refrigeration system of the present invention: the working medium in described generator is binary or non-azeotropic mixed working medium more than binary.
As the further improvement of absorption compression auto-cascading refrigeration system of the present invention: described compressor is frequency-changeable compressor.
A kind of using method that absorbs compression auto-cascading refrigeration system: step is as follows:
By heating binary or non-azeotropic mixed working medium more than binary, produce low boiling gas-phase working medium I more than needed and higher boiling liquid phase working fluid I more than needed; Gas-phase working medium I more than needed low boiling, after the condensation of external source, is carried out to gas-liquid separation, produce low boiling gas-phase working medium II more than needed and higher boiling liquid phase working fluid II more than needed; Heat exchange mutually between described low boiling gas-phase working medium II more than needed and higher boiling liquid phase working fluid II more than needed, becomes liquid phase working fluid I by gas-phase working medium II condensation more than needed low boiling, and higher boiling liquid phase working fluid II heat absorption more than needed evaporation becomes gas-phase working medium I; Liquid phase working fluid I after heat release cooling and heat absorption evaporation step, becomes gas-phase working medium II successively; Gas-phase working medium II by with the mutual heat exchange of liquid phase working fluid I after, be mixed into low boiling gas-phase working medium III more than needed with gas-phase working medium I; After higher boiling liquid phase working fluid I heat release more than needed, temperature reduces, then mixes mutually with low boiling gas-phase working medium III more than needed, and absorbs low boiling gas-phase working medium III more than needed, becomes liquid phase working fluid II; After the liquid phase working fluid I heat exchange more than needed of liquid phase working fluid II and higher boiling, again become binary or non-azeotropic mixed working medium more than binary, and carry out the circulation of next round.
The present invention absorb compression auto-cascading refrigeration system with using method compared with existing auto-cascading refrigeration system, have the following advantages:
1) with electrically driven (operated) compression compared with the cascade system, can adopt low grade heat energy and electric energy to combine driving simultaneously, can reduce high-grade energy consumption, increase the utilization rate to low-grade energy.
2) what drive with heat is absorption compared with the cascade system, can utilize frequency-changeable compressor to carry out supercharging to evaporimeter low-pressure gas out, has avoided multistage overlapping, has simplified system configuration, and the adjusting of evaporating temperature is also more flexible.
3), compared with the folded system of absorption compression runback driving with existing electricity, heat integration, the solution absorption cycle in the present invention has been born more driving merit, has therefore further reduced compressor power consumption and pressure ratio, has expanded the utilization rate to low-grade energy.In addition, the present invention has the compression of absorption and absorption two kinds of mode of operations, and according to circumstances switchover operation, as when required evaporating temperature is higher or external source temperature is lower, the absorption work pattern that system can drive by heat, thus greatly reduced high-grade power consumption.
Accompanying drawing explanation
Below in conjunction with accompanying drawing, the specific embodiment of the present invention is described in further detail.
Fig. 1 is a kind of structural representation that the present invention absorbs compression auto-cascading refrigeration system;
Fig. 2 is another structural representation that the present invention absorbs compression auto-cascading refrigeration system.
The specific embodiment
Embodiment 1, as Fig. 1 has provided a kind of absorption compression auto-cascading refrigeration system, comprise generator 1, solution heat exchanger 2, absorber 4, solution pump 5, condenser 6, gas-liquid separator 7, evaporative condenser 8, the first gas-liquid heat-exchanges 11, evaporimeter 13 and compressor 14.
One end of the pyrosol pipeline of the taphole of generator 1 and solution heat exchanger 2 is interconnected, and other one end of the pyrosol pipeline of solution heat exchanger 2 and the solution inlet port of absorber 4 are interconnected, between the pyrosol pipe end of solution heat exchanger 2 and the solution inlet port of absorber 4, be provided with first throttle valve 3, one end of the cryogenic fluid pipeline of the taphole of absorber 4 and solution heat exchanger 2 is interconnected, and other one end of the cryogenic fluid pipeline of solution heat exchanger 2 and the solution inlet port of generator 1 are interconnected, between the cryogenic fluid pipe end of the taphole of absorber 4 and solution heat exchanger 2, be provided with solution pump 5, one end of the condensation pipe of the gas vent of generator 1 and condenser 6 is interconnected, and other one end of the condensation pipe of condenser 6 and the moist steam import of gas-liquid separator 7 are interconnected, one end of the high temperature refrigerant pipeline of the gas vent of gas-liquid separator 7 and evaporative condenser 8 is interconnected, one end of the high-temp liquid pipeline of other one end of the high temperature refrigerant pipeline of evaporative condenser 8 and the first gas-liquid heat-exchange 11 is interconnected, one end of other one end of the high-temp liquid pipeline of the first gas-liquid heat-exchange 11 and the evaporation tubes of evaporimeter 13 is interconnected, one end of the cryogenic gas pipeline of other one end of the evaporation tubes of evaporimeter 13 and the first gas-liquid heat-exchange 11 is interconnected, other one end of the cryogenic gas pipeline of the first gas-liquid heat-exchange 11 and the gas access of compressor 14 are interconnected, between the port of other one end of the high-temp liquid pipeline of the first gas-liquid heat-exchange 11 and the evaporation tubes of evaporimeter 13, be provided with the 3rd choke valve 12, one end of the evaporation tubes of the taphole of gas-liquid separator 7 and evaporative condenser 8 is interconnected, between the port of the evaporation tubes of the taphole of gas-liquid separator 7 and evaporative condenser 8, be provided with the second choke valve 9, other one end of the evaporation tubes of the gas vent of compressor 14 and evaporative condenser 8 is interconnected with the gas feed of absorber 4 respectively.
Between the gas vent of the gas feed of compressor 14 and compressor 14, be connected with two-port valve 10.
Above-described compressor 14 is frequency-changeable compressor, can control according to setting outlet pressure.Working medium in above-described generator 1 is binary or non-azeotropic mixed working medium more than binary, the solution of the interior absorption mixed working fluid of absorber 1 gas can only consist of the liquid phase component that is absorbed gas itself, also can comprise other substantially unvaporized third party's component in operating temperature range.Mixed working fluid used can be selected from aspects such as operating temperature, thermophysical property and technical-economic indexes.
During actual use, the mixed working fluid in generator 1, concrete steps are as follows:
One, absorption pressure compressed mode (as shown in Figure 1, compressor 14 is opened, and two-port valve 10 cuts out):
1, external heat source under high pressure heats generator 1, makes the mixed working fluid in generator 1 be subject to thermal evaporation, produces low boiling gas-phase working medium I more than needed and higher boiling liquid phase working fluid I more than needed;
1.1, low boiling gas phase I more than needed:
1.1.1, low boiling gas phase I more than needed flows out from the gas vent of generator 1, enters in the condensation pipe of condenser 6, by external source, to condensation pipe condensation, the low boiling gas phase I temperature more than needed in condensation pipe reduces, mass dryness fraction declines, and becomes moist steam I;
1.1.2, moist steam I enters gas-liquid separator 7, gas-liquid separator 7 carries out gas-liquid separation by moist steam I, produces low boiling gas-phase working medium II more than needed and higher boiling liquid phase working fluid II more than needed;
1.1.3, low boiling gas-phase working medium II more than needed flows out from the gas vent of gas-liquid separator 7, enter in the condensation pipe of evaporative condenser 8, low boiling gas-phase working medium II more than needed is in the condensation pipe of evaporative condenser 8 after heat release, temperature reduces, and condensation becomes and the isocyatic liquid phase working fluid I of this gas-phase working medium;
Meanwhile, higher boiling liquid phase working fluid II more than needed flows out from the liquid outlet of gas-liquid separator 7, and by the second choke valve 9, pressure is pressure from high pressure drops to, the evaporation tubes that simultaneous temperature enters evaporative condenser 8 after declining; In the evaporation tubes of evaporative condenser 8, (the low boiling gas-phase working medium II heat release in the condensation pipe of evaporative condenser 8 of having more than needed after higher boiling liquid phase working fluid II heat absorption more than needed evaporation, by higher boiling liquid phase working fluid II more than needed, absorbed), temperature raises, and becomes gas-phase working medium I;
1.1.4, liquid phase working fluid I enters the high-temp liquid pipeline of the first gas-liquid heat-exchange 11, after heat release, temperature further reduces, then by the 3rd choke valve 12, pressure is reduced to low pressure from high pressure, the evaporation tubes that simultaneous temperature enters evaporimeter 13 after declining, and heat absorption evaporation in the evaporation tubes of evaporimeter 13, temperature raises, and becomes gas-phase working medium II;
1.1.5, gas-phase working medium II enters the cryogenic gas pipeline of the first gas-liquid heat-exchange 11, heat absorption is (in step 1.1.4, the heat release in the high-temp liquid pipeline of the first gas-liquid heat-exchange 11 of liquid phase working fluid I) after temperature further raise, then enter the gas feed of compressor 14, by compressor 14 from low-pressure charging to pressure, finally from the gas vent of compressor 14, flow out;
1.1.6, the low boiling gas-phase working medium III more than needed that gas-phase working medium I and gas-phase working medium II are depressed in being mixed into;
1.2, higher boiling liquid phase working fluid I more than needed:
1.2.1, the higher boiling liquid phase working fluid I more than needed that flows out from the liquid outlet of generator 1 flows into the high-temp liquid pipeline of solution heat exchanger 2, after heat release, temperature reduces, then enters absorber 4 after being depressured to middle pressure by first throttle valve 3;
2, the low boiling gas-phase working medium III more than needed of depressing in enters absorber 4, mixing mutually, is absorbed with the higher boiling liquid phase working fluid I more than needed flowing into from absorber 4 liquid-inlets, become liquid phase working fluid II, and the absorption latent heat of emitting is taken away by external source;
3, liquid phase working fluid II enters by solution pump 5 from the liquid outlet of absorber 4 flows out, and after being pressurizeed, becomes highly pressurised liquid by solution pump 5;
4, the highly pressurised liquid being pressurizeed by solution pump 5 enters the low-temperature liquid pipe of solution heat exchanger 2, after heat absorption, temperature raises (in step 1.2.1, higher boiling liquid phase working fluid I heat release in the high-temp liquid pipeline of solution heat exchanger 2 more than needed of flowing out from the liquid outlet of generator 1), and flow into generator 1 from the liquid-inlet of generator 1.
When two, absorption compression auto-cascading refrigeration system of the present invention is worked under absorption mode (compressor 14 cuts out, and two-port valve 10 is opened), job step is as follows:
1, external heat source under high pressure heats generator 1, makes the mixed working fluid in generator 1 be subject to thermal evaporation, produces low boiling gas-phase working medium I more than needed and higher boiling liquid phase working fluid I more than needed;
1.1, low boiling gas phase I more than needed:
1.1.1, low boiling gas phase I more than needed flows out from the gas vent of generator 1, enters in the condensation pipe of condenser 6, by external source, to condensation pipe condensation, the low boiling gas phase I temperature more than needed in condensation pipe reduces, mass dryness fraction declines, and becomes moist steam I;
1.1.2, moist steam I enters gas-liquid separator 7, gas-liquid separator 7 carries out gas-liquid separation by moist steam I, produces low boiling gas-phase working medium II more than needed and higher boiling liquid phase working fluid II more than needed;
1.1.3, low boiling gas-phase working medium II more than needed flows out from the gas vent of gas-liquid separator 7, enter in the condensation pipe of evaporative condenser 8, low boiling gas-phase working medium II more than needed is in the condensation pipe of evaporative condenser 8 after heat release, temperature reduces, and condensation becomes and the isocyatic liquid phase working fluid I of this gas-phase working medium;
Meanwhile, higher boiling liquid phase working fluid II more than needed flows out from the liquid outlet of gas-liquid separator 7, and by the second choke valve 9, pressure drops to low pressure from high pressure, the evaporation tubes that simultaneous temperature enters evaporative condenser 8 after declining; In the evaporation tubes of evaporative condenser 8, (the low boiling gas-phase working medium II heat release in the condensation pipe of evaporative condenser 8 of having more than needed after higher boiling liquid phase working fluid II heat absorption more than needed evaporation, by higher boiling liquid phase working fluid II more than needed, absorbed), temperature raises, and becomes gas-phase working medium I;
1.1.4, liquid phase working fluid I enters the high-temp liquid pipeline of the first gas-liquid heat-exchange 11, after heat release, temperature further reduces, then by the 3rd choke valve 12, pressure is reduced to low pressure from high pressure, the evaporation tubes that simultaneous temperature enters evaporimeter 13 after declining, and heat absorption evaporation in the evaporation tubes of evaporimeter 13, temperature raises, and becomes gas-phase working medium II;
1.1.5, gas-phase working medium II enters the cryogenic gas pipeline of the first gas-liquid heat-exchange 11, heat absorption is (in step 1.1.4, the heat release in the high-temp liquid pipeline of the first gas-liquid heat-exchange 11 of liquid phase working fluid I) after temperature further raise, then by the rear inflow absorber 4 of two-port valve 10;
1.1.6, gas-phase working medium I and gas-phase working medium II are mixed into the low boiling gas-phase working medium III more than needed under low pressure;
1.2, higher boiling liquid phase working fluid I more than needed:
1.2.1, the higher boiling liquid phase working fluid I more than needed that flows out from the liquid outlet of generator 1 flows into the high-temp liquid pipeline of solution heat exchanger 2, after heat release, temperature reduces, then enters absorber 4 after being depressured to low pressure by first throttle valve 3;
2, the low boiling gas-phase working medium III more than needed of depressing in enters absorber 4, mixing mutually, is absorbed with the higher boiling liquid phase working fluid I more than needed flowing into from absorber 4 liquid-inlets, become liquid phase working fluid II, and the absorption latent heat of emitting is taken away by external source;
3, liquid phase working fluid II enters by solution pump 5 from the liquid outlet of absorber 4 flows out, and after being pressurizeed, becomes highly pressurised liquid by solution pump 5;
4, the highly pressurised liquid being pressurizeed by solution pump 5 enters the low-temperature liquid pipe of solution heat exchanger 2, after heat absorption, temperature raises (in step 1.2.1, higher boiling liquid phase working fluid I heat release in the high-temp liquid pipeline of solution heat exchanger 2 more than needed of flowing out from the liquid outlet of generator 1), and flow into generator 1 from the liquid-inlet of generator 1.
Absorbing compression mode of operation and absorption mode of operation can switch according to practical operation situation, and when required evaporating temperature is lower or sink temperature is higher, system is changeable for absorbing the operation of compression mode of operation; When required evaporating temperature is higher or sink temperature is lower, system is changeable is absorption mode of operation operation.
Embodiment 2, as Fig. 2, system is by generator 1, solution heat exchanger 2, first throttle valve 3, absorber 4, solution pump 5, condenser 6, gas-liquid separator 7, evaporative condenser 8, the second choke valve 9, two-port valve 10, the first gas-liquid heat-exchanges 11, the 3rd choke valve 12, evaporimeter 13, compressor 14 and the second gas-liquid heat-exchange 15 form.
For reducing the caloric receptivity of generator, raising system COP, in embodiment 2, absorption compression auto-cascading refrigeration system of the present invention adopts in the configure base of embodiment 1, employing arranges the set-up mode of the second gas-liquid heat-exchange 15 between generator 1, solution heat exchanger 2 and condenser 6:, the cryogenic fluid pipeline of solution heat exchanger 2 and the low-temperature liquid pipe of the second gas-liquid heat-exchange 15 interconnect, and the low-temperature liquid pipe of the second gas-liquid heat-exchange 15 is connected with the solution inlet port of generator 1; The gas vent of generator 1 is connected with the hot-gas channel of the second gas-liquid heat-exchange 15, and the condensation pipe of the hot-gas channel of the second gas-liquid heat-exchange 15 and condenser 6 interconnects.All the other connected modes are identical with embodiment 1.
The present embodiment workflow and the difference of embodiment 1 as follows:
1, the low boiling gas-phase working medium more than needed flowing out from the gas vent of generator 1 enters the hot-gas channel of the second gas-liquid heat-exchange 15, with the solution heat exchange entering in the low-temperature liquid pipe of the second gas-liquid heat-exchange 15 simultaneously, after heat release by partial condensation, temperature reduces, mass dryness fraction declines, enter again condenser 6 and in its condensation pipe by the further partial condensation of external source, temperature, mass dryness fraction further decline, and enter gas-liquid separator 7 after becoming moist steam;
2, after being pressurizeed by solution pump 5, the liquid phase working fluid that the liquid outlet of absorber 2 flows into becomes highly pressurised liquid, enter again the low-temperature liquid pipe of solution heat exchanger 2, after heat absorption, temperature raises, enter again the low-temperature liquid pipe of the second gas-liquid heat-exchange 15, after heat absorption, temperature raises, and finally from the liquid-inlet of generator 1, flows into generator 1.
All the other workflows are identical with embodiment 1.
Embodiment 2 set up the second gas-liquid heat-exchange 15, reclaimed the condensation latent heat that low boiling gas-phase working medium more than needed that generator gas vent flows out is discharged when partial condensation, and the heat exhaustion while having reduced in generator heated solution, can improve system COP.
The calculating parameter of embodiment 1 and embodiment 2 in Table 1(for 1kg evaporimeter mix refrigerant).Design condition is: 22 ℃ of environment temperatures, working medium is R23/R134a, the maximum temperature of required driving heat source is higher than 64.4 ℃, the minimum temperature of required cooling fluid is lower than 24.2 ℃, the generation pressure of generator is 3Mpa, the pressure of absorber is 1.6Mpa, and the evaporating pressure of evaporimeter is 0.6Mpa, and cold-producing medium evaporating temperature is within the scope of-25.4 ℃~-3.9 ℃.The COP(that embodiment 1 calculates is defined as the ratio of evaporation endothermic amount and compressor power consumption and generator caloric receptivity) be 29.4%, system for fire effect (the cold fire that is defined as evaporimeter output is used and all fiery ratios with input of system) be 23.45%; Embodiment 2 is compared with embodiment 1, reclaimed a part of heat of generator exports gas phase mixed working fluid when partial condensation for heating the solution that enters generator, therefore required generator caloric receptivity decreases, make COP and system fire effect be elevated to respectively 36.3% and 26.7%, show that this improvement has certain actual effect.Under table 1 the same terms, compare the absorption auto-cascading refrigeration system of the compression absorbing coupling of patent CN102759218 proposition, the present invention reduces to 59.5% by consuming at least heat of 143.4kJ/kg by compressor work consumption more, compressor pressure ratio is reduced to 2.67 from 5 simultaneously, increased the dependence to low-grade energy, reduce the consumption to high-grade electric energy, thereby effectively realized initial object of the present invention.In sum, one proposed by the invention absorbs compression auto-cascading refrigeration system, has greater efficiency, retain the flexibility of compressor boost, reduced the dependence to compressor work, can also improve low-grade energy utilization rate, compressor exhaust temperature is low, has good using value.
In above embodiment, can consider the rationally design parameter of definite system of the factors such as concrete service condition and requirement, technical and economic performance, to take into account applicability and the economy of system.
The heating power result of calculation (1kg evaporimeter mix refrigerant) of table 1 embodiment 1, embodiment 2
Finally, it is also to be noted that, what more than enumerate is only several specific embodiments of the present invention.Obviously, the invention is not restricted to above embodiment, can also have many distortion.All distortion that those of ordinary skill in the art can directly derive or associate from content disclosed by the invention, all should think protection scope of the present invention.

Claims (7)

1. absorb compression auto-cascading refrigeration system, comprise generator (1), solution heat exchanger (2), absorber (4), solution pump (5), condenser (6), gas-liquid separator (7), evaporative condenser (8), the first gas-liquid heat-exchange (11), evaporimeter (13) and compressor (14); It is characterized in that: one end of the pyrosol pipeline of the taphole of described generator (1) and solution heat exchanger (2) is interconnected, the solution inlet port of other one end of the pyrosol pipeline of solution heat exchanger (2) and absorber (4) is interconnected;
One end of the cryogenic fluid pipeline of the taphole of described absorber (4) and solution heat exchanger (2) is interconnected, and the solution inlet port of other one end of the cryogenic fluid pipeline of described solution heat exchanger (2) and generator (1) is interconnected;
One end of the condensation pipe of the gas vent of described generator (1) and condenser (6) is interconnected, and the moist steam import of other one end of the condensation pipe of described condenser (6) and gas-liquid separator (7) is interconnected;
One end of the high temperature refrigerant pipeline of the gas vent of described gas-liquid separator (7) and evaporative condenser (8) is interconnected, one end of the high-temp liquid pipeline of other one end of the high temperature refrigerant pipeline of evaporative condenser (8) and the first gas-liquid heat-exchange (11) is interconnected, one end of the evaporation tubes of other one end of the high-temp liquid pipeline of described the first gas-liquid heat-exchange (11) and evaporimeter (13) is interconnected, one end of the cryogenic gas pipeline of other one end of the evaporation tubes of evaporimeter (13) and the first gas-liquid heat-exchange (11) is interconnected, the gas access of other one end of the cryogenic gas pipeline of the first gas-liquid heat-exchange (11) and compressor (14) is interconnected,
One end of the evaporation tubes of the taphole of described gas-liquid separator (7) and evaporative condenser (8) is interconnected;
Other one end of the evaporation tubes of the gas vent of described compressor (14) and evaporative condenser (8) is interconnected with the gas feed of absorber (4) respectively.
2. absorption compression auto-cascading refrigeration system according to claim 1, is characterized in that: between the pyrosol pipe end of described solution heat exchanger (2) and the solution inlet port of absorber (4), be provided with first throttle valve (3);
Between the cryogenic fluid pipe end of the taphole of described absorber (4) and solution heat exchanger (2), be provided with solution pump (5);
Between the port of the evaporation tubes of other one end of the high-temp liquid pipeline of described the first gas-liquid heat-exchange (11) and evaporimeter (13), be provided with the 3rd choke valve (12);
Between the port of the evaporation tubes of the taphole of described gas-liquid separator (7) and evaporative condenser (8), be provided with the second choke valve (9).
3. absorption compression auto-cascading refrigeration system according to claim 2, is characterized in that: between the gas feed of described compressor (14) and the gas vent of compressor (14), be connected with two-port valve (10).
4. absorption compression auto-cascading refrigeration system according to claim 3, is characterized in that: between described generator (1), solution heat exchanger (2) and condenser (6), be provided with the second gas-liquid heat-exchange (15);
The low-temperature liquid pipe of the cryogenic fluid pipeline of described solution heat exchanger (2) and the second gas-liquid heat-exchange (15) interconnects, and the low-temperature liquid pipe of described the second gas-liquid heat-exchange (15) is connected with the solution inlet port of generator (1);
The gas vent of generator (1) is connected with the hot-gas channel of the second gas-liquid heat-exchange (15), and the condensation pipe of the hot-gas channel of described the second gas-liquid heat-exchange (15) and condenser (6) interconnects.
5. absorption compression auto-cascading refrigeration system according to claim 4, is characterized in that: the working medium in described generator (1) is binary or non-azeotropic mixed working medium more than binary.
6. absorption compression auto-cascading refrigeration system according to claim 5, is characterized in that: described compressor (14) is frequency-changeable compressor.
7. a using method that absorbs compression auto-cascading refrigeration system, is characterized in that: step is as follows:
By heating binary or non-azeotropic mixed working medium more than binary, produce low boiling gas-phase working medium I more than needed and higher boiling liquid phase working fluid I more than needed;
Gas-phase working medium I more than needed low boiling, after the condensation of external source, is carried out to gas-liquid separation, produce low boiling gas-phase working medium II more than needed and higher boiling liquid phase working fluid II more than needed;
Heat exchange mutually between described low boiling gas-phase working medium II more than needed and higher boiling liquid phase working fluid II more than needed, becomes liquid phase working fluid I by gas-phase working medium II condensation more than needed low boiling, and higher boiling liquid phase working fluid II heat absorption more than needed evaporation becomes gas-phase working medium I;
Liquid phase working fluid I after heat release cooling and heat absorption evaporation step, becomes gas-phase working medium II successively;
Gas-phase working medium II by with the mutual heat exchange of liquid phase working fluid I after, be mixed into low boiling gas-phase working medium III more than needed with gas-phase working medium I;
After higher boiling liquid phase working fluid I heat release more than needed, temperature reduces, then mixes mutually with low boiling gas-phase working medium III more than needed, and absorbs low boiling gas-phase working medium III more than needed, becomes liquid phase working fluid II;
After the liquid phase working fluid I heat exchange more than needed of liquid phase working fluid II and higher boiling, again become binary or non-azeotropic mixed working medium more than binary, and carry out the circulation of next round.
CN201310695791.XA 2013-12-17 2013-12-17 Absorption compression type automatic-overlapping refrigerating system and use method Active CN103743150B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201310695791.XA CN103743150B (en) 2013-12-17 2013-12-17 Absorption compression type automatic-overlapping refrigerating system and use method

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201310695791.XA CN103743150B (en) 2013-12-17 2013-12-17 Absorption compression type automatic-overlapping refrigerating system and use method

Publications (2)

Publication Number Publication Date
CN103743150A true CN103743150A (en) 2014-04-23
CN103743150B CN103743150B (en) 2017-01-18

Family

ID=50500197

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201310695791.XA Active CN103743150B (en) 2013-12-17 2013-12-17 Absorption compression type automatic-overlapping refrigerating system and use method

Country Status (1)

Country Link
CN (1) CN103743150B (en)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104006570A (en) * 2014-06-05 2014-08-27 中国科学院工程热物理研究所 Direct and reverse cycle coupling based absorption and compression combined type refrigerating system and method
CN104214988A (en) * 2014-09-03 2014-12-17 中国科学院工程热物理研究所 Absorption refrigeration system with dual temperature heat sources
CN104482688A (en) * 2014-11-27 2015-04-01 华南理工大学 Solar absorbing compressing combined type refrigerating system and method
CN105180507A (en) * 2015-09-23 2015-12-23 内蒙古科技大学 Self-overlapping vortex tube absorbing refrigerating system
CN105823265A (en) * 2015-04-13 2016-08-03 李华玉 First-kind thermally driven compression-absorption heat pump
CN105910341A (en) * 2015-04-13 2016-08-31 李华玉 First kind thermal driving compression-absorption heat pump
CN106016821A (en) * 2015-04-13 2016-10-12 李华玉 First-class heat drive compression-absorption type heat pump
CN106091474A (en) * 2016-06-17 2016-11-09 珠海格力电器股份有限公司 Ammonia absorption compression-type refrigeration/heat pump and heat-exchange method
CN110056936A (en) * 2019-04-24 2019-07-26 东北大学 A kind of low ebb electric heat storage cascade type heat pump heating system and mode
CN110173929A (en) * 2019-04-29 2019-08-27 同济大学 A kind of absorption of band machinery recuperation of heat-compression mixture circulatory system and working method
CN110325806A (en) * 2016-10-05 2019-10-11 江森自控科技公司 Heat pump for HVAC & R system
CN111457616A (en) * 2020-03-30 2020-07-28 普泛能源技术研究院(北京)有限公司 Improved method for enhancing heat exchange of generator, generator and absorption refrigeration and heat pump

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4031712A (en) * 1975-12-04 1977-06-28 The University Of Delaware Combined absorption and vapor-compression refrigeration system
DE4415199A1 (en) * 1994-04-30 1995-11-02 Inst Luft Und Kaeltetechnik Gm Refrigerating plant using absorption principle
JP2004138316A (en) * 2002-10-17 2004-05-13 Tokyo Gas Co Ltd Combined refrigeration device
CN101886857A (en) * 2010-07-08 2010-11-17 张端桥 Parallel connection type solar collector tube generator and absorbing type refrigeration air-conditioning system formed by same
CN102230686A (en) * 2011-06-12 2011-11-02 浙江理工大学 Lithium bromide absorption-compression type series boosting refrigeration/heating pump system
CN102759218A (en) * 2012-07-23 2012-10-31 浙江大学 Auto-cascade low-temperature refrigerator of compressing, absorbing and coupling

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4031712A (en) * 1975-12-04 1977-06-28 The University Of Delaware Combined absorption and vapor-compression refrigeration system
DE4415199A1 (en) * 1994-04-30 1995-11-02 Inst Luft Und Kaeltetechnik Gm Refrigerating plant using absorption principle
JP2004138316A (en) * 2002-10-17 2004-05-13 Tokyo Gas Co Ltd Combined refrigeration device
CN101886857A (en) * 2010-07-08 2010-11-17 张端桥 Parallel connection type solar collector tube generator and absorbing type refrigeration air-conditioning system formed by same
CN102230686A (en) * 2011-06-12 2011-11-02 浙江理工大学 Lithium bromide absorption-compression type series boosting refrigeration/heating pump system
CN102759218A (en) * 2012-07-23 2012-10-31 浙江大学 Auto-cascade low-temperature refrigerator of compressing, absorbing and coupling

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104006570B (en) * 2014-06-05 2016-10-19 中国科学院工程热物理研究所 Absorption based on forward and reverse cycle coupling-compression combined formula refrigeration system and method
CN104006570A (en) * 2014-06-05 2014-08-27 中国科学院工程热物理研究所 Direct and reverse cycle coupling based absorption and compression combined type refrigerating system and method
CN104214988A (en) * 2014-09-03 2014-12-17 中国科学院工程热物理研究所 Absorption refrigeration system with dual temperature heat sources
CN104214988B (en) * 2014-09-03 2016-05-04 中国科学院工程热物理研究所 A kind of two temperature-heat-source absorption system
CN104482688A (en) * 2014-11-27 2015-04-01 华南理工大学 Solar absorbing compressing combined type refrigerating system and method
CN105910341B (en) * 2015-04-13 2020-04-07 李华玉 First-class thermally driven compression-absorption heat pump
CN105910341A (en) * 2015-04-13 2016-08-31 李华玉 First kind thermal driving compression-absorption heat pump
CN106016821A (en) * 2015-04-13 2016-10-12 李华玉 First-class heat drive compression-absorption type heat pump
CN105823265A (en) * 2015-04-13 2016-08-03 李华玉 First-kind thermally driven compression-absorption heat pump
CN105823265B (en) * 2015-04-13 2020-04-07 李华玉 First-class thermally driven compression-absorption heat pump
CN105180507A (en) * 2015-09-23 2015-12-23 内蒙古科技大学 Self-overlapping vortex tube absorbing refrigerating system
CN105180507B (en) * 2015-09-23 2019-10-01 内蒙古科技大学 A kind of Auto-cascade cycle vortex tube absorbent refrigeration system
CN106091474A (en) * 2016-06-17 2016-11-09 珠海格力电器股份有限公司 Ammonia absorption compression-type refrigeration/heat pump and heat-exchange method
CN106091474B (en) * 2016-06-17 2018-09-18 珠海格力电器股份有限公司 Ammonium hydroxide Absorption-Compression refrigeration/heat pump system and heat-exchange method
CN110325806A (en) * 2016-10-05 2019-10-11 江森自控科技公司 Heat pump for HVAC & R system
CN110056936A (en) * 2019-04-24 2019-07-26 东北大学 A kind of low ebb electric heat storage cascade type heat pump heating system and mode
CN110056936B (en) * 2019-04-24 2020-09-15 东北大学 Off-peak electricity heat storage cascade heat pump heat supply method
CN110173929A (en) * 2019-04-29 2019-08-27 同济大学 A kind of absorption of band machinery recuperation of heat-compression mixture circulatory system and working method
CN110173929B (en) * 2019-04-29 2020-11-27 同济大学 Absorption-compression mixed circulation system with mechanical heat recovery and working method
CN111457616A (en) * 2020-03-30 2020-07-28 普泛能源技术研究院(北京)有限公司 Improved method for enhancing heat exchange of generator, generator and absorption refrigeration and heat pump
CN111457616B (en) * 2020-03-30 2021-02-12 普泛能源技术研究院(北京)有限公司 Improved method for enhancing heat exchange of generator, generator and absorption refrigeration and heat pump

Also Published As

Publication number Publication date
CN103743150B (en) 2017-01-18

Similar Documents

Publication Publication Date Title
CN103743150A (en) Absorption compression type automatic-overlapping refrigerating system and use method
CN103629860B (en) Trans-critical cycle CO 2cool and thermal power combined cycle system
CN102128508B (en) Ejector throttling and vapor supplementing system and heat pump or refrigerating system vapor supplementing method
CN104929706A (en) Combined circulating energy supply system
CN102650478B (en) Trans-critical-compression/absorption composite refrigeration device utilizing low-grade heat
CN101691960B (en) Three-pipe heating and reclaiming air-conditioning system
CN105041471A (en) Combined circulation energy supplying system
CN201666686U (en) Throttling air supply system with ejectors
CN101603749B (en) Auto-cascade injection low-temperature refrigeration circulating device
Xue et al. A review of cryogenic power generation cycles with liquefied natural gas cold energy utilization
CN104963732A (en) Combined circulating energy supplying system
CN103759449B (en) The two-stage steam compression type circulatory system of dual jet synergy
CN101825372A (en) Device and method for combined ejection refrigeration and vapor compression refrigeration cycle
CN102620461A (en) Auto-cascade jet type refrigerator
CN202254464U (en) Trans-critical carbon dioxide (CO2) circulating refrigeration system
CN104948245A (en) Combined-cycle energy supply system
CN110345690B (en) Double-ejector synergistic refrigeration cycle system for double-temperature refrigerator and working method
CN104929704A (en) Combined circulating energy supply system
CN103940134B (en) Vapor-compression refrigerant cycle work of expansion recovery system
CN105041472A (en) Combined cycle energy supply system
CN110057124A (en) A kind of part superposition type quotient is super to use CO2Trans-critical cycle double-stage compressive refrigerating system
CN102384604A (en) Double-temperature-heat-source injection-type refrigeration system
CN104989472A (en) Combined cycle energy supply system
CN104963733A (en) Combined cycle energy supply system
CN202284866U (en) Double-temperature heat source spray type refrigeration system

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant
TR01 Transfer of patent right
TR01 Transfer of patent right

Effective date of registration: 20200907

Address after: 404601 group 6, Jiuliu village, Yongle Town, Fengjie County, Chongqing

Patentee after: Chongqing Kuizhou Cold Chain Logistics Co.,Ltd.

Address before: Hangzhou City, Zhejiang province 310018 Xiasha Higher Education Park No. 2 Street No. 5

Patentee before: Zhejiang University of Technology