CN115468327A - Self-overlapping refrigerating system with grading dephlegmator - Google Patents
Self-overlapping refrigerating system with grading dephlegmator Download PDFInfo
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- CN115468327A CN115468327A CN202211145868.1A CN202211145868A CN115468327A CN 115468327 A CN115468327 A CN 115468327A CN 202211145868 A CN202211145868 A CN 202211145868A CN 115468327 A CN115468327 A CN 115468327A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/06—Superheaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
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- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention provides a self-cascade refrigeration system with a fractional condenser, which comprises a compressor, wherein the compressor adopts a fractional compressor and is provided with a first-stage air suction port a, a second-stage air suction port b and an air exhaust port c; the inlet of the refrigerant working medium channel of the condenser is connected with the exhaust port c of the compressor and is used for condensing the high-temperature high-pressure gaseous mixed refrigerant working medium discharged by the compressor into a gas-liquid two-phase mixed refrigerant working medium; the inlet of the gas-liquid separator is connected with the outlet of the refrigerant working medium channel of the condenser and is used for carrying out flash separation on the gas-liquid two-phase mixed refrigerant working medium discharged from the condenser; a graded dephlegmator component is arranged above the inside of the gas-liquid separator and is used for rectifying and purifying the gaseous mixed refrigerant working medium after flash evaporation in the gas-liquid separator, so that the pressure ratio of the mixed working medium rich in high-component branches in the compression process can be effectively reduced, the low-temperature refrigeration capacity gradient utilization is realized, and the lower refrigeration temperature is obtained; the scheme has the advantages of simple structure, obvious energy-saving effect and reliable and stable operation.
Description
Technical Field
The invention belongs to a low-temperature throttling refrigeration technology of mixed working media, and particularly relates to a self-cascade refrigeration system with a graded dephlegmator.
Background
The self-cascade refrigerating system is a refrigerating system which uses non-azeotropic mixed working medium and realizes multi-stage cascade by a single compressor to obtain low temperature below 60 ℃ below zero, and the system has the advantages of simple structure, reliable operation, low cost and the like, and is widely applied to the fields of low temperature refrigeration and the like. Therefore, the self-cascade refrigeration system has important significance for saving energy and protecting the environment. The traditional single-stage self-cascade refrigeration cycle adopts single-stage compression and has low-temperature performance requirements, so that the compression ratio of the working medium flowing out from the bottom of the gas-liquid separator and rich in high-boiling-point component branches is higher, the total energy consumption of the compressor is higher, and the refrigeration efficiency obtained by the traditional single-stage compression cycle is lower and the refrigeration temperature is limited. The traditional self-cascade technology also has the problems of low separation efficiency and the like because a phase separator is adopted to separate mixed refrigerant, and in order to solve the problems, on one hand, the binary non-azeotropic mixed working medium which is effectively separated from the self-cascade refrigeration cycle by adopting two-stage or multi-stage separation is adopted to improve the purity of low-boiling-point components, so that the lower evaporation temperature can be realized, but the pressure ratio is larger, so that the energy consumption of the system is higher, on the other hand, the high-efficiency separation of the mixed working medium is realized by adopting a rectifying device to improve the self-cascade refrigeration cycle, but when the environmental temperature is increased, the rectifying effect is poor and the like.
In the prior art, a refrigeration system with two compressors connected in series is taken as an example, so that a high-boiling-point working medium absorbs heat in a low-temperature stage condenser, is directly mixed with a working medium at the outlet of a first-stage compressor, and then enters a second-stage compressor, the suction temperature of the second-stage compressor can be reduced, and the exhaust temperature of the second-stage compressor is reduced. However, the system needs two compressors connected in series, which increases the complexity and cost of the system, and the gas-liquid separator in the system is not provided with an effective component separation device, so that the efficiency of separating high and low boiling point components by a partial condenser is low, and the purity of the low boiling point components cannot be effectively improved, so that the refrigeration temperature which can be prepared by the system is limited. In particular, the refrigeration system adopting the serial connection mode of two compressors in series has the defects that the lubricating oil carried by the working medium rich in high-boiling-point components only enters the second-stage compressor, and the working medium rich in low-boiling-point components entering the first-stage compressor does not carry the lubricating oil through gas-liquid separation, so that the internal moving parts of the first-stage compressor cannot be lubricated, the faults of dry burning of the compressor, insufficient oil seal and the like occur, and the damage of the first-stage compressor is aggravated.
Disclosure of Invention
The invention aims to solve the problems in the prior art, and provides a self-cascade refrigeration system with a fractional condenser, which is applied to low-temperature throttling refrigeration in a specific place and can realize high-efficiency separation of high and low boiling points and low-temperature refrigeration.
In order to achieve the purpose, the invention adopts the following technical scheme: a self-cascade refrigeration system with a fractional condenser comprises a compressor, a condenser and a condenser, wherein the compressor is provided with a first-stage air suction port a, a second-stage air suction port b and an air exhaust port c and adopts a fractional compressor; the inlet of the refrigerant working medium channel of the condenser is connected with the exhaust port c of the compressor and is used for condensing the high-temperature high-pressure gaseous mixed refrigerant working medium discharged by the compressor into a gas-liquid two-phase mixed refrigerant working medium; the inlet of the gas-liquid separator is connected with the outlet of the refrigerant working medium channel of the condenser and is used for carrying out flash separation on the gas-liquid two-phase mixed refrigerant working medium discharged by the condenser; the gas-liquid separator is internally provided with a grading dephlegmator component above and used for rectifying and purifying the gas-state mixed refrigerant working medium after the flash evaporation in the gas-liquid separator, wherein the gas-phase refrigerant working medium which flows out of the top of the gas-liquid separator and is rectified and purified is mixed with a part of liquid-phase refrigerant working medium discharged from an outlet at the bottom of the gas-liquid separator, and finally enters a first-stage air suction port a of the compressor through a first refrigerant working medium pipeline of the grading dephlegmator component; and the other part of liquid-phase refrigerant working medium discharged from the outlet at the bottom of the gas-liquid separator finally enters a second-stage air suction port b of the compressor through a second refrigerant working medium pipeline of the fractional condenser assembly, so that fractional compression is realized.
Preferably, the fractional condenser assembly comprises a first fractional condenser and a second fractional condenser, and the first fractional condenser is positioned below the second fractional condenser; mixing the gas-phase refrigerant working medium flowing out of the top of the gas-liquid separator with a part of liquid-phase refrigerant working medium discharged from the outlet at the bottom of the gas-liquid separator; the refrigerant enters a first-stage air suction port a of the compressor after passing through a refrigerant working medium pipeline of a second sub-condenser; and the other part of the liquid-phase refrigerant working medium discharged from the bottom of the gas-liquid separator enters a secondary air suction port b of the compressor through a refrigerant working medium pipeline of the first sub-condenser.
Preferably, the system also comprises a first heat regenerator, which is used for enabling the refrigerant working medium passing through the refrigerant working medium channel of the second partial condenser to enter a first-stage air suction port a of the compressor after being superheated.
Preferably, the first heat regenerator comprises a low-temperature side channel and a high-temperature side channel, an outlet of a refrigerant working medium channel of the second sub-condenser is connected with an inlet of the low-temperature side channel of the first heat regenerator, and an outlet of the low-temperature side channel of the first heat regenerator is connected with a first-stage air suction port a of the compressor, so that the refrigerant working medium discharged by the second sub-condenser enters the first-stage air suction port a of the compressor after being superheated by the first heat regenerator; and an inlet of a high-temperature side channel of the first heat regenerator is connected with an outlet at the bottom of the gas-liquid separator.
Preferably, the outlet of the high-temperature side channel of the first heat regenerator is divided into two branches, wherein the refrigerant working medium flowing out of the first branch enters the refrigerant working medium channel of the first sub-condenser, and the refrigerant working medium flowing out of the second branch is mixed with the refrigerant working medium flowing out of the outlet at the top of the gas-liquid separator and then enters the refrigerant working medium channel of the second sub-condenser.
Preferably, the first branch path is sequentially provided with a first throttling component and an evaporative condenser, an inlet of the first throttling component is connected with an outlet of a high-temperature side channel of the first heat regenerator, an outlet of the first throttling component is connected with an inlet of a low-temperature side channel of the evaporative condenser, and an outlet of the low-temperature side channel of the evaporative condenser is connected with an inlet of a refrigerant working medium channel of the first sub-condenser.
Preferably, an inlet of a high-temperature side channel of the evaporative condenser is connected with an outlet at the top of the gas-liquid separator, an outlet of the high-temperature side channel of the evaporative condenser is connected with an inlet of a high-temperature side channel of the second heat regenerator, an outlet of the high-temperature side channel of the second heat regenerator is connected with an inlet of a refrigerant working medium channel of the evaporator through a third throttling component, an outlet of the refrigerant working medium channel of the evaporator is connected with an inlet of a low-temperature side channel of the second heat regenerator, and the refrigerant working medium at the outlet of the low-temperature side channel of the second heat regenerator and part of liquid-phase refrigerant working medium discharged from an outlet at the bottom of the gas-liquid separator are throttled and mixed to enter a refrigerant working medium channel of the second partial condenser.
As a preferred scheme, the refrigerant working medium is a binary or more than binary non-azeotropic mixed refrigerant working medium formed by mixing a high-boiling point refrigerant working medium and a low-boiling point refrigerant working medium, the low-boiling point refrigerant working medium adopts an HC or HFC refrigerant working medium, and the low-boiling point refrigerant working medium is one or more of R1150, R50 or R23; the high boiling point refrigerant working medium is HC or HFC refrigerant working medium, and the high boiling point refrigerant working medium is one or more of R134a, R152a, R600 and R600 a.
Advantageous effects
The invention can realize high-efficiency separation of high and low boiling points and low-temperature refrigeration, and is different from the common technical route in the prior art, the scheme adopts a specific technical route, utilizes a stage compressor with two-stage air suction ports, ensures that most of mixed working medium rich in high boiling point components from the bottom of a gas-liquid separator flows into the stage compressor only through the medium-pressure air suction port of the compressor to realize the compression process of low compression ratio, and ensures that all the mixed working medium rich in low boiling point components from the top of the gas-liquid separator and a small part of the mixed working medium rich in high boiling point components from the bottom of the gas-liquid separator flow into the stage compressor only through the low-pressure air suction port of the compressor to realize the compression process of high compression ratio, thereby realizing the step compression process of the mixed working medium, reducing the compression ratio of the compressor and obviously reducing the total energy consumption of the compressor.
Secondly, this scheme adopts the first branch condenser that stacks of height and second branch condenser structural design thought, realizes the step rectification purification process to the low boiling point component of gaseous mixed working medium in the vapour and liquid separator and to the cold volume cascade utilization of the low temperature of different temperature levels to obtain lower refrigerating temperature, and promote refrigeration efficiency.
Thirdly, according to the scheme, the first heat regenerator is arranged at the outlet at the bottom of the gas-liquid separator, so that the supercooling degree of the liquid mixed working medium at the outlet at the bottom of the gas-liquid separator is increased, the mixed working medium entering a first air suction port of the staged compressor is ensured to be in an overheated or saturated steam state, and the effects of improving the refrigeration efficiency and ensuring the dry compression process of the compressor are achieved.
Drawings
In order to more clearly illustrate the embodiments of the invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the invention, and it is obvious for those skilled in the art that other drawings can be obtained based on these drawings without creative efforts.
FIG. 1 is a schematic diagram of a self-cascade refrigeration system with a staged dephlegmator of the present invention;
the labels in the figure are: 1. the system comprises a compressor, a condenser, a gas-liquid separator, a first throttling component, a second throttling component, a third throttling component, an evaporator, a second heat regenerator, a second sub-condenser, a first heat regenerator, a first throttling component and a second throttling component, wherein the compressor is 2, the condenser is 3, the gas-liquid separator is 4, the first throttling component is 5, the evaporative condenser is 6, the second heat regenerator is 7, the third throttling component is 8, the evaporator is 9, the second sub-condenser is 10, the first sub-condenser is 11, the first heat regenerator is 12 and the second throttling component; a. a first-stage air inlet, a second-stage air inlet, a third-stage air outlet and an air outlet.
Detailed Description
The invention is described in detail below by way of exemplary embodiments. It should be understood, however, that elements, structures and features of one embodiment may be beneficially incorporated in other embodiments without further recitation.
It should be noted that: unless defined otherwise, technical or scientific terms used herein shall have the ordinary meaning as understood by one of ordinary skill in the art to which this invention belongs. The use of the terms "a" and "an" or "the" and similar referents in the description and claims of the present invention are not to be construed as limiting in number, but rather as indicating the presence of at least one. The word "comprise" or "comprises", and the like, indicates that the element or item listed before "comprises" or "comprising" covers the element or item listed after "comprising" or "comprises" and its equivalents, but does not exclude other elements or items having the same function.
The embodiment provides a self-cascade refrigeration system with a fractional condenser, which comprises a compressor 1, a condenser 2, a gas-liquid separator 3, a first throttling component 4, an evaporative condenser 5, a second heat regenerator 6, a third throttling component 7, an evaporator 8, a second fractional condenser 9, a first fractional condenser 10, a first heat regenerator 11 and a second throttling component 12.
In the embodiment, the compressor 1 is a staged compressor, and is provided with a primary air suction port a, a secondary air suction port b and a high-pressure exhaust port c; the first-stage air suction port a is a low-pressure air suction port, the second-stage air suction port b is a medium-pressure air suction port, the first-stage air suction port a and the second-stage air suction port b arranged on the compressor 1 can realize the step compression process that working media flowing out of the bottom and the top of the gas-liquid separator 3 respectively enter the compressor 1, an exhaust port c of the compressor 1 is connected with an inlet of the gas-liquid separator 3 through the condenser 2, the gas-liquid separator 3 is also provided with a top outlet and a bottom outlet, a top outlet of the gas-liquid separator 3, a high-temperature side channel of the evaporative condenser 5, a high-temperature side channel of the second heat regenerator 6, the third throttling part 7 and an inlet of the evaporator 8 are sequentially connected in series, and an outlet of the evaporator 8 is connected with an outlet pipeline of the second throttling part 12 through a low-temperature side channel of the second heat regenerator 6; the bottom outlet of the gas-liquid separator 3 is connected with the high-temperature side channel inlet of the first heat regenerator 11, and the high-temperature side channel outlet of the first heat regenerator 11 is divided into two branches; a branch is connected with the inlet of the first throttling component 4, the outlet of the first throttling component 4 is connected with the inlet of the low-temperature side channel of the evaporative condenser 5, the outlet of the low-temperature side channel of the evaporative condenser 5 is connected with the inlet of the first sub-condenser 10, and the outlet of the first sub-condenser 10 is connected with the secondary air suction port b of the compressor 1; the other branch of the high temperature side channel outlet of the first heat regenerator 11 is connected with the inlet of the second throttling component 12, the outlet of the second throttling component 12 is connected with the inlet of the second partial condenser 9, the outlet of the second partial condenser 9 is connected with the low temperature side channel inlet of the first heat regenerator 11, and the low temperature side channel outlet of the first heat regenerator 11 is connected to the first stage air suction port a of the compressor 1. Wherein the outlet of the low temperature channel of the second regenerator 6 is connected to the conduit between the outlet of the second throttling element 12 and the inlet of the second partial condenser 9. The first throttling part 4 is provided on the pipe between the gas-liquid separator 3 and the evaporative condenser 5, the second throttling part 12 is provided on the pipe between the gas-liquid separator 3 and the second subcondenser 9, and the third throttling part 7 is provided on the connecting pipe between the evaporator 8 and the high temperature side pipe of the second regenerator 6.
In the scheme, an exhaust port c of a compressor 1 is connected with an inlet of a gas-liquid separator 3 through a condenser 2, so that a high-temperature high-pressure gaseous mixed refrigerant working medium discharged from the exhaust port c of the compressor 1 is condensed by the condenser 2 to release heat into a high-temperature high-pressure gas-liquid two-phase mixed refrigerant working medium to enter the gas-liquid separator 3 for flash separation, a secondary air suction port b of the compressor 1 is connected with a low-temperature side channel of an evaporative condenser 5 through a first sub-condenser 10, a part of liquid mixed refrigerant working medium flowing out from the bottom of the gas-liquid separator 3 and the gaseous mixed refrigerant working medium flowing out from the top of the gas-liquid separator 3 exchange heat through the evaporative condenser 5, and finally flows into the compressor 1 through a secondary air suction port b of the compressor 1 to complete a compression process with a low compression ratio, a primary air suction port a of the compressor 1 is connected with a second sub-condenser 9 through a first regenerator 11, so that the gaseous refrigerant working medium from the second regenerator 6 and the liquid refrigerant working medium throttled by a second throttling component 12 are mixed and finally enter a primary air suction port a first sub-condenser 9 to complete a compression process with a high compression ratio, and thus the staged compression process is finally completed in the compressor 1. And the inlet of the refrigerant working medium channel of the condenser 2 is connected with the exhaust port c of the compressor 1 and is used for condensing the high-temperature high-pressure gaseous mixed refrigerant working medium discharged by the compressor 1 into a gas-liquid two-phase mixed refrigerant working medium.
The scheme is that the compressor 1 utilizes the characteristic that non-azeotropic mixed working media are flash-evaporated and separated into gas-phase and liquid-phase mixed working media in the gas-liquid separator 3, the working media rich in high-boiling-point component branches are high in evaporation temperature after throttling, the evaporation pressure of the working media is also high, so that the gas-phase mixed working media entering the secondary suction port b of the compressor 1 have higher purity, the working media rich in low-boiling-point component branches are low in evaporation temperature after throttling, the evaporation pressure of the working media is also low, only the working media flow into the primary suction port a of the compressor 1, and the two branch working media complete fractional compression in the compressor 1, thereby reducing the energy consumption of the compressor and preparing lower refrigeration temperature.
The gas-liquid separator 3 functions to: the high-temperature high-pressure gas-liquid two-phase mixed working medium from the condenser 2 is separated into a gas-phase mixed working medium rich in low-boiling point components and flows out from a top working medium outlet of the high-boiling point components, and a liquid-phase mixed working medium rich in high-boiling point components and flows out from a bottom working medium outlet of the high-boiling point components, meanwhile, the gas-liquid separator 3 is provided with a fractional condensation structure, and the fractional condensation structure is a fractional condenser component, so that the gas-phase working medium rich in low-boiling point components and separated by the gas-liquid separator 3 is partially condensed, and therefore, a saturated gas-phase refrigerant working medium rich in high-purity low-boiling point components flows out from the top of the gas-liquid separator 3, wherein the condensed liquid-phase refrigerant working medium flows back to the bottom of the gas-liquid separator 3 and flows out from the bottom of the gas-liquid separator 3 together with the liquid-phase refrigerant working medium rich in high-boiling point components and separated by flash evaporation.
In this embodiment, a refrigerant working medium inlet of the gas-liquid separator 3 is connected to an exhaust port c of the compressor 1 through the condenser 2, so that the high-temperature high-pressure gas-liquid two-phase mixed refrigerant working medium from the condenser 2 is flash evaporated and separated in the gas-liquid separator 3 into a liquid-phase mixed refrigerant working medium rich in a high boiling point component and a gas-phase mixed refrigerant working medium rich in a low boiling point component, and a fractional condenser assembly is disposed above the inside of the gas-liquid separator 3 and used for rectifying and purifying the flash evaporated gas-phase mixed refrigerant working medium in the gas-liquid separator 3. The gas-phase refrigerant working medium rich in low-boiling-point components and separated by the gas-liquid separator 3 through flash evaporation is partially condensed under the action of the fractional condenser component, and the obtained gas-phase refrigerant working medium with higher purity and low-boiling-point components flows out from the top outlet of the gas-liquid separator 3; the liquid refrigerant working medium condensed by the fractional condenser component flows back to the bottom of the gas-liquid separator 3 to be mixed with the liquid refrigerant working medium which is separated by the gas-liquid separator 3 through flash evaporation and is rich in high boiling point components, and the mixture is discharged through a bottom outlet of the gas-liquid separator 3.
In the scheme, the fractional condenser component comprises a first fractional condenser 10 and a second fractional condenser 9, and the first fractional condenser 10 is positioned below the second fractional condenser 9. The second sub-condenser 9 has the functions of: the gas phase mixed working medium which flows out from the working medium outlet at the top of the gas-liquid separator 3 and is rich in low boiling point components can be superheated after flowing through the second heat regenerator 6 and then continuously superheated through the second sub-condenser 9, so that low-pressure superheated steam is obtained and enters the first-stage air suction port a of the compressor 1, and the first sub-condenser 10 has the functions of: liquid mixed working medium which flows out from a working medium outlet at the bottom of the gas-liquid separator 3 and is rich in high-boiling point components is evaporated and absorbs heat through an evaporation side of an evaporative condenser 5 and then is continuously overheated, and then obtained medium-pressure superheated steam enters a secondary air suction port b of the compressor 1, so that the staged compression process of the two branch working media is realized, and the energy consumption of the compressor 1 is reduced.
In one particular embodiment: the first sub-condenser 10 and the second sub-condenser 9 are both arranged in the upper space in the gas-liquid separator 3, and working medium steam of the gas-liquid separator 3 flows through the first sub-condenser 10 from bottom to top to undergo a first-stage rectification and purification process, and then flows through the second sub-condenser 9 to undergo a second-stage rectification and purification process; the first sub-condenser 10 and the second sub-condenser 9 arranged in the gas-liquid separator 3 realize the step rectification and purification effect on the low boiling point component of the gaseous mixed working medium in the gas-liquid separator 3 and realize the step utilization of low-temperature cold energy at different temperature levels.
In this embodiment, the first heat regenerator 11 is disposed between the gas-liquid separator 3 and the second throttling component 12, so that after the liquid mixed refrigerant working medium rich in high boiling point components from the bottom of the gas-liquid separator 3 is subcooled at the high temperature side of the first heat regenerator 11, a part of the mixed refrigerant working medium flows into the second throttling component 12 and is mixed with the refrigerant working medium rich in low boiling point components superheated by the second heat regenerator 6, and then flows into the second sub-condenser 9, thereby achieving the rectification requirement of the second sub-condenser 9, the first heat regenerator 11 is disposed between the second sub-condenser 9 and the compressor 1, and the first heat regenerator 11 is disposed to aim at: the mixed refrigerant refrigerating system is used for recovering the low-temperature cold quantity of the mixed refrigerant working medium at the outlet of the second sub-condenser 9, simultaneously ensures that the mixed refrigerant working medium before entering the air suction port a of the compressor 1 is in a saturated steam state or an overheated state, and avoids the wet compression process in the compression process of the compressor 1. After the gaseous refrigerant working medium rich in the low-boiling point component from the top outlet of the gas-liquid separator 3 absorbs heat and is cooled by the second sub-condenser 9, the refrigerant working medium in the second sub-condenser 9 is guaranteed to be overheated, and therefore the dryness requirement of the compressor 1 in the compression process is guaranteed.
In this embodiment, the liquid working medium rich in high boiling point component flowing out from the first heat regenerator 11 is divided into two branches: the liquid working medium of the first branch enters the evaporative condenser 5 after being throttled and cooled by the first throttling component 4, absorbs the condensation heat of the gaseous refrigerant working medium rich in low-boiling-point components from the gas-liquid separator 3, enters the first sub-condenser 10 to realize the first-stage rectification and purification of the gaseous mixed refrigerant working medium in the gas-liquid separator 3, and then enters the second-stage air suction port b of the compressor 1 to complete the compression process with low compression ratio; the second branch liquid refrigerant is throttled, cooled and depressurized by a second throttling part 12, then mixed with the refrigerant from a second heat regenerator 6 and enters a second sub-condenser 9 to realize second-stage rectification and purification of the gaseous mixed refrigerant in the gas-liquid separator 3, and finally flows into the compressor 1 through a first-stage air suction port a of the compressor 1 after absorbing heat by a first heat regenerator 11 to complete the compression process with high compression ratio.
In this embodiment, a gas-phase mixed refrigerant working medium rich in low-boiling point components flowing out from a working medium outlet at the top of the gas-liquid separator 3 is condensed by the evaporative condenser 5, then enters the second heat regenerator 6 for supercooling at the high temperature side, is throttled by the third throttling member 7, obtains a low-pressure two-phase refrigerant working medium, flows into the evaporator 8 for evaporation and heat absorption, obtains a saturated gas-phase refrigerant working medium, enters the second heat regenerator 6 for superheating at the low temperature side, then is mixed with a working medium throttled and depressurized by the second throttling member 12, the mixed gas-liquid two-phase refrigerant working medium enters the second condenser 9 for superheating at the low temperature side, then enters the first suction port a of the compressor 1 for superheating at the low temperature side, obtains a medium-pressure two-phase refrigerant working medium rich in high-boiling point components flowing out from a working medium outlet at the bottom of the gas-liquid mixed refrigerant working medium, is subcooled by the first heat regenerator 11 for splitting, one of the medium-pressure two-phase refrigerant working medium flows into the first throttling member 4 for throttling, then enters the evaporative condenser 5 for evaporation and is superheated, the first sub-condenser 10 for superheating, the obtained medium-pressure superheated steam enters the second suction port b of the compressor 1 for being compressed into high-temperature high-pressure gas, and at the same time, the other branch flows out of the second throttling member 11, flows into the second throttling member 12 for superheating and then enters the second mixed refrigerant working medium-pressure gas, and is superheated steam, and is decompressed by the second condenser 6 for being superheated, and is sucked into the first sub-pressure mixed refrigerant condenser 6 for being superheated. Compared with the prior art, the multistage compressor is adopted, and the refrigerant working medium flow direction is adopted, so that sufficient lubrication of the compressor can be ensured. (for the refrigeration system of two compressors in series connection in the prior art, in the running process of the system, the lubricating oil of the system is often wrapped by the refrigerant and discharged out of the compressor, and is carried back to the compressor by the refrigerant after circulation, the refrigerant has two phases in the circulation process of the system, namely, liquid refrigerant and vapor refrigerant, and the lubricating oil is basically in the liquid state, when the refrigerant is changed from the liquid state to the vapor state in the gas-liquid separator, the lubricating oil can be separated from the vapor refrigerant and does not flow along with the vapor refrigerant, if the lubricating oil carried by the separated liquid refrigerant only enters the secondary compressor and does not enter the primary compressor, the lubricating oil can cause insufficient lubrication of the internal moving parts of the primary compressor in the using process, the faults of dry burning and insufficient oil sealing of the compressor occur, and the damage of the primary compressor can be aggravated.)
The working principle of the scheme is as follows: superheated steam flowing out of an exhaust port c of a compressor 1 is partially condensed by a condenser 2 and then enters a gas-liquid separator 3 with a double-stage dephlegmator structure for flash separation and purification, refrigerant working medium steam entering the gas-liquid separator 3 flows through a first-stage rectification purification process outside a first dephlegmator 10 from bottom to top and then flows through a second-stage rectification purification process outside a second dephlegmator 9, so that saturated gas-phase refrigerant working medium rich in high-purity low-boiling-point components flows out of the top of the gas-liquid separator 3, and condensed liquid refrigerant working medium flows back to the bottom of the gas-liquid separator 3 and flows out of the bottom of the gas-liquid separator 3 together with flash separated liquid working medium rich in high-boiling-point components. Thereby mixed refrigerant working medium is divided into two branches, and the flow direction of one of them working medium is: the saturated gaseous refrigerant which flows out from the top of the gas-liquid separator 3 and is rich in high-purity low-boiling point components enters the high-temperature side channel of the condensing evaporator 5 to be partially condensed into gas-liquid two-phase refrigerant, enters the high-temperature side channel of the second heat regenerator 6 for supercooling, enters the third throttling part 7 for throttling and pressure reduction to obtain low-pressure two-phase refrigerant, enters the evaporator 8 for evaporation and heat absorption to realize low-temperature refrigeration, the saturated gaseous refrigerant flowing out of the evaporator 8 is overheated through the low-temperature side channel of the second heat regenerator 6, is mixed with the liquid refrigerant throttled by the second throttling part 12, then enters the second sub-condenser 9 for overheating and the low-temperature side channel of the first heat regenerator 11 for overheating, and the low-pressure gaseous refrigerant flowing out of the first heat regenerator 11 is sucked into the compressor 1 through the first air suction port a of the compressor 1 to complete the compression process with high compression ratio.
Meanwhile, after the saturated liquid working medium rich in high-boiling point components flowing out of the other branch from the bottom of the gas-liquid separator 3 flows into a high-temperature side channel of the first heat regenerator 11 for supercooling, the obtained liquid working medium rich in high-boiling point components is divided into two branches, wherein one branch flows to the first throttling part 4 for throttling and depressurizing, the flowing medium-pressure two-phase refrigerant working medium exchanges heat through a low-temperature side channel of the evaporative condenser 5, medium-pressure superheated steam obtained after heat exchange in the first sub-condenser 10 enters a secondary air suction port b of the compressor 1, meanwhile, the other branch flows to the second throttling part 12 for throttling, cooling and depressurizing, then is mixed with the gas refrigerant working medium from the second heat regenerator 6 and enters the second sub-condenser 9, so that second-stage rectification and purification of the gas-state mixed working medium in the gas-liquid separator 3 are realized, and then the gas is absorbed by the low-temperature side channel of the first heat regenerator 11 and flows into a primary air suction port a of the compressor 1 to finish the compression process with a high compression ratio, thereby realizing a step compression process in the compressor 1, and completing a cycle. The refrigeration cycle system can effectively reduce the pressure ratio of the compressor in the compression process of the mixed working medium rich in the high-component branch.
The scheme realizes the cascade compression effect of the working medium by one stage compressor, reduces the compression ratio of the compressor, and reduces the energy consumption and the exhaust temperature of the compressor; the step rectification purification of the gaseous mixed working medium is realized by arranging a two-stage partial condenser, the step utilization of low-temperature cold energy is realized, the purity of low-boiling-point components is improved, and lower refrigeration temperature is obtained; the supercooling degree of the mixed working medium is increased and the wet compression process of the mixed working medium is avoided by arranging the first heat regenerator 11. The system has the advantages of simple structure, obvious energy-saving effect, reliable and stable operation and wide application prospect.
In the scheme, the adopted working medium is a binary or more-than-binary non-azeotropic mixed working medium formed by mixing a high-boiling point working medium and a low-boiling point working medium, the low-boiling point working medium is HC or HFC working media such as R1150, R50 and R23, and the high-boiling point working medium is HC or HFC working media such as R134a, R152a, R600 and R600 a.
Although the present invention has been described with reference to a preferred embodiment, it should be understood that various changes, substitutions and alterations can be made herein without departing from the spirit and scope of the invention as defined by the appended claims.
Claims (8)
1. The utility model provides a take fractional condenser's from overlapping refrigerating system which characterized in that: comprises that
The compressor is a classified compressor and is provided with a first-stage air suction port a, a second-stage air suction port b and an air exhaust port c;
the inlet of the refrigerant working medium channel of the condenser is connected with the exhaust port c of the compressor and is used for condensing the high-temperature high-pressure gaseous mixed refrigerant working medium discharged by the compressor into a gas-liquid two-phase mixed refrigerant working medium;
the inlet of the gas-liquid separator is connected with the outlet of the refrigerant working medium channel of the condenser and is used for carrying out flash separation on the gas-liquid two-phase mixed refrigerant working medium discharged from the condenser; a graded dephlegmator component is arranged above the inside of the gas-liquid separator and is used for rectifying and purifying the gas mixed refrigerant working medium after the flash evaporation in the gas-liquid separator;
the rectified and purified gas-phase refrigerant working medium flowing out of the top of the gas-liquid separator is mixed with a part of liquid-phase refrigerant working medium discharged from an outlet at the bottom of the gas-liquid separator, and finally enters a first-stage air suction port a of the compressor through a first refrigerant working medium pipeline of the fractional condenser assembly; and the other part of liquid-phase refrigerant working medium discharged from the outlet at the bottom of the gas-liquid separator finally enters a second-stage air suction port b of the compressor through a second refrigerant working medium pipeline of the fractional condenser assembly, so that fractional compression is realized.
2. A self-cascade refrigeration system with a staged dephlegmator as in claim 1 wherein: the fractional condenser component comprises a first fractional condenser and a second fractional condenser, and the first fractional condenser is positioned below the second fractional condenser; the refrigerant working medium is formed by mixing the gas-phase refrigerant working medium flowing out of the top of the gas-liquid separator and a part of liquid-phase refrigerant working medium discharged from an outlet at the bottom of the gas-liquid separator; the refrigerant enters a first-stage air suction port a of the compressor after passing through a refrigerant working medium pipeline of a second sub-condenser; and the other part of the liquid-phase refrigerant working medium discharged from the bottom of the gas-liquid separator enters a secondary air suction port b of the compressor through a refrigerant working medium pipeline of the first sub-condenser.
3. A self-cascade refrigeration system with a fractional condenser as set forth in claim 2, wherein: the first heat regenerator is used for leading the refrigerant working medium passing through the refrigerant working medium channel of the second sub-condenser to enter a first-stage air suction port a of the compressor finally after being overheated.
4. A self-cascade refrigeration system with a fractional condenser as set forth in claim 3, wherein: the first heat regenerator comprises a low-temperature side channel and a high-temperature side channel, the outlet of the refrigerant working medium channel of the second sub-condenser is connected with the inlet of the low-temperature side channel of the first heat regenerator, and the outlet of the low-temperature side channel of the first heat regenerator is connected with the primary air suction port a of the compressor, so that the refrigerant working medium discharged by the second sub-condenser enters the primary air suction port a of the compressor after being overheated by the first heat regenerator; and an inlet of a high-temperature side channel of the first heat regenerator is connected with an outlet at the bottom of the gas-liquid separator.
5. The self-cascade refrigeration system of claim 4 having a staged dephlegmator, wherein: the outlet of the high-temperature side channel of the first heat regenerator is divided into two branches, wherein the refrigerant working medium flowing out of the first branch enters the refrigerant working medium channel of the first sub-condenser, and the refrigerant working medium flowing out of the second branch is mixed with the refrigerant working medium flowing out of the outlet at the top of the gas-liquid separator and then enters the refrigerant working medium channel of the second sub-condenser.
6. A self-cascade refrigeration system with a fractional condenser as set forth in claim 5, wherein: the first branch is sequentially provided with a first throttling component and an evaporative condenser, an inlet of the first throttling component is connected with an outlet of a high-temperature side channel of the first heat regenerator, an outlet of the first throttling component is connected with an inlet of a low-temperature side channel of the evaporative condenser, and an outlet of the low-temperature side channel of the evaporative condenser is connected with an inlet of a refrigerant working medium channel of the first sub-condenser.
7. A self-cascade refrigeration system with a staged dephlegmator as in claim 6 wherein: the high-temperature side channel inlet of the evaporative condenser is connected with the top outlet of the gas-liquid separator, the high-temperature side channel outlet of the evaporative condenser is connected with the high-temperature side channel inlet of the second heat regenerator, the high-temperature side channel outlet of the second heat regenerator is connected with the refrigerant working medium channel inlet of the evaporator through the third throttling component, the refrigerant working medium channel outlet of the evaporator is connected with the low-temperature side channel inlet of the second heat regenerator, and the refrigerant working medium at the low-temperature side channel outlet of the second heat regenerator and part of liquid-phase refrigerant working medium discharged from the bottom outlet of the gas-liquid separator are throttled and then mixed to enter the refrigerant working medium channel of the second partial condenser.
8. The self-cascade refrigeration system with a staged dephlegmator of any of claims 1 to 7, wherein: the refrigerant working medium is a binary or more than binary non-azeotropic mixed refrigerant working medium formed by mixing a high-boiling point refrigerant working medium and a low-boiling point refrigerant working medium, the low-boiling point refrigerant working medium adopts an HC or HFC refrigerant working medium, and the low-boiling point refrigerant working medium is one or more of R1150, R50 or R23; the high boiling point refrigerant working medium is HC or HFC refrigerant working medium, and the high boiling point refrigerant working medium is one or more of R134a, R152a, R600 and R600 a.
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