CN110822879B - Drying and dehumidifying method based on non-azeotropic mixed working medium heat pump system - Google Patents
Drying and dehumidifying method based on non-azeotropic mixed working medium heat pump system Download PDFInfo
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- 238000001035 drying Methods 0.000 title claims abstract description 126
- 238000000034 method Methods 0.000 title claims abstract description 39
- 238000009835 boiling Methods 0.000 claims abstract description 332
- 238000009833 condensation Methods 0.000 claims abstract description 80
- 230000005494 condensation Effects 0.000 claims abstract description 80
- 238000001704 evaporation Methods 0.000 claims abstract description 75
- 230000008020 evaporation Effects 0.000 claims abstract description 72
- 230000006835 compression Effects 0.000 claims abstract description 42
- 238000007906 compression Methods 0.000 claims abstract description 42
- 239000007788 liquid Substances 0.000 claims abstract description 41
- 238000000926 separation method Methods 0.000 claims abstract description 35
- 238000010438 heat treatment Methods 0.000 claims abstract description 17
- 230000004044 response Effects 0.000 claims abstract description 16
- 238000007791 dehumidification Methods 0.000 claims description 57
- 238000011084 recovery Methods 0.000 claims description 38
- 238000010521 absorption reaction Methods 0.000 claims description 22
- 238000001816 cooling Methods 0.000 claims description 17
- 230000008929 regeneration Effects 0.000 claims description 17
- 238000011069 regeneration method Methods 0.000 claims description 17
- 238000002309 gasification Methods 0.000 claims description 12
- 238000010981 drying operation Methods 0.000 claims description 9
- 239000012530 fluid Substances 0.000 claims description 6
- 238000002360 preparation method Methods 0.000 claims description 6
- 230000001172 regenerating effect Effects 0.000 claims description 5
- 239000003507 refrigerant Substances 0.000 description 35
- 239000000463 material Substances 0.000 description 9
- 238000010586 diagram Methods 0.000 description 7
- 230000007246 mechanism Effects 0.000 description 7
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 7
- 230000009467 reduction Effects 0.000 description 4
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- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 239000000243 solution Substances 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 230000002427 irreversible effect Effects 0.000 description 1
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- 238000010257 thawing Methods 0.000 description 1
- 238000010792 warming Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F26—DRYING
- F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
- F26B21/00—Arrangements or duct systems, e.g. in combination with pallet boxes, for supplying and controlling air or gases for drying solid materials or objects
- F26B21/06—Controlling, e.g. regulating, parameters of gas supply
- F26B21/08—Humidity
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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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
- F26—DRYING
- F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
- F26B21/00—Arrangements or duct systems, e.g. in combination with pallet boxes, for supplying and controlling air or gases for drying solid materials or objects
- F26B21/06—Controlling, e.g. regulating, parameters of gas supply
- F26B21/10—Temperature; Pressure
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- General Engineering & Computer Science (AREA)
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Abstract
A drying and dehumidifying method based on a non-azeotropic mixed working medium heat pump system is characterized in that mixed working medium discharged from an exhaust end of a compression unit passes through a condensation unit and a gas separation unit to form gas-liquid separation of high/low boiling working medium; the high-boiling working medium passes through the high-boiling throttling unit and then is communicated with the non-azeotropic mixed working medium heat exchange unit, and after the high-boiling working medium and the low-boiling working medium in the non-azeotropic mixed working medium heat exchange unit carry out first heat exchange, the high-boiling working medium and the low-boiling working medium respectively are communicated with the heat return unit to carry out second heat exchange; then, the high-boiling working medium returns to the air suction end of the compression unit, and the low-boiling working medium which completes the second heat exchange sequentially passes through the low-boiling throttling unit, the low-boiling evaporation unit and the low-boiling gas sub-unit and returns to the air inlet end of the middle cavity of the compression unit; the invention relates to a drying and dehumidifying method based on a non-azeotropic mixed working medium heat pump system, which establishes three-level heat treatment responses of drying, drying + dehumidifying and deep dehumidifying in the system by arranging a non-azeotropic mixed working medium heat exchange unit and matching with corresponding units arranged in front of and behind the non-azeotropic mixed working medium heat exchange unit.
Description
Technical Field
The invention belongs to the field of drying and dehumidification based on a heat pump, and particularly relates to a drying and dehumidification method based on a non-azeotropic mixed working medium heat pump system.
Background
Routine data experiments show that:
1. under the low-temperature working condition, under the condition that the temperature of the dry air inlet balls in the closed space is the same, along with the reduction of the temperature of the wet air inlet balls in the closed space, the dehumidification amount of the evaporator in the closed space is reduced, the latent cooling amount is reduced, the sensible cooling amount is increased, and the total cooling amount is gradually reduced. When the temperature of inlet air wet bulb in the closed space reaches below 16 ℃, the latent cooling capacity is reduced to the minimum. 2. When the temperature of the inlet air wet bulb in the closed space is below 16 ℃, the outlet air relative humidity of the evaporator is sharply reduced to be close to the dew point temperature of air, so that the dehumidification amount is reduced to the minimum, and then the dehumidification amount of the indoor evaporator is only slowly fluctuated along with the temperature change of the inlet air wet bulb in the closed space. 3. Under the low-temperature working condition, the dehumidification amount of the evaporator is reduced along with the reduction of the temperature of the inlet air wet bulb in the closed space, the reduction degree has a threshold value, the temperature of the inlet air wet bulb in the closed space is not reduced after being lower than 16 ℃, and the temperature of the outlet air wet bulb is lower than the dew point temperature of saturated wet air.
The application numbers are: 201610606271.0, discloses a 'non-azeotropic mixed working medium solution defrosting, freezing and regenerating large temperature difference heat pump unit', which comprises a compressor, a gas-liquid separator with an outlet connected with an air suction port of the compressor, a second user end heat exchanger connected with an air exhaust port of the compressor and used for condensing high boiling point components in a mixed refrigerant, and a fractionator; the gas phase outlet of the fractionator is connected with a first user end heat exchanger for condensing the refrigerant rich in the low boiling point component, the refrigerant outlet of the first user end heat exchanger is connected with a second throttling valve and an electromagnetic valve, the second throttling valve is connected with the electromagnetic valve in parallel and then connected with the inlet of the solution regeneration heat exchanger, and the outlet of the solution regeneration heat exchanger is connected with a first interface of a four-way reversing valve.
The application numbers are: the invention application of 201610878972.X discloses a 'refrigerating system suitable for non-azeotropic refrigerants', which comprises a refrigerating compressor, a four-way reversing valve, two heat exchangers, a throttling mechanism and a plurality of one-way valves, wherein the refrigerating compressor, the four-way reversing valve, the two heat exchangers, the throttling mechanism and the one-way valves jointly form a refrigerant cycle to realize the dual purposes of refrigerating and cooling and heating by a heat pump; the throttle mechanism can be a one-way throttle mechanism or a two-way throttle mechanism or a refrigerating throttle mechanism and a heating throttle mechanism are adopted simultaneously. The four-way reversing valve and each one-way valve jointly realize the flow reversing of the refrigerant, so that the flow direction of the refrigerant in the first heat exchanger and the second heat exchanger and the flow direction of a heat exchange medium of the refrigerant are always in a counter-flow state no matter in a refrigerating working condition or a heating working condition, the heat transfer temperature difference is improved, particularly when a non-azeotropic refrigerant is adopted, the temperature change characteristic of the refrigerant can be fully utilized, and meanwhile, the high efficiency and the energy conservation of the refrigerating working condition and the heating working condition are realized.
The application numbers are: 201810499113.9, discloses a self-cascade refrigeration system and a control method thereof, the refrigeration system comprises an evaporator, a condenser, a two-phase injection compressor, three electronic expansion valves, two gas-liquid separators, two evaporative condensers and a heat regenerator; the refrigerating system adopts a binary non-azeotropic mixed working medium, and uses a two-phase jet compressor, so that on one hand, irreversible loss in a primary throttling process and a heat exchange process in an evaporative condenser is reduced, and the energy efficiency of the system is improved, on the other hand, the exhaust temperature of the compressor can be effectively reduced, and the reliability of the compressor is improved; the refrigerating system comprises two gas-liquid separators which are connected in series so as to realize two-stage separation of mixed working media, improve the content of low-temperature working media in the evaporator, effectively improve the evaporation pressure and reduce the pressure ratio of the compressor, thereby reducing the power consumption of the compressor.
Disclosure of Invention
In order to solve the problems, the invention provides a drying and dehumidifying method based on a non-azeotropic mixed working medium heat pump system, which has the following technical scheme:
a drying and dehumidifying method based on a non-azeotropic mixed working medium heat pump system is characterized in that:
in the heat pump system, the mixed working medium discharged from the exhaust end of the compression unit passes through the arranged condensation unit and the gas separation unit to form gas-liquid separation of the low-boiling working medium and the high-boiling working medium;
after passing through the high-boiling throttling unit, the liquid high-boiling working medium leads to the non-azeotropic mixed working medium heat exchange unit and carries out first heat exchange with the gaseous low-boiling working medium leading to the non-azeotropic mixed working medium heat exchange unit, and then leads to the regenerative unit for carrying out second heat exchange of the high-boiling working medium and the low-boiling working medium;
the high-boiling working medium which completes the second heat exchange returns to the air suction end of the compression unit, and the low-boiling working medium which completes the second heat exchange sequentially passes through the low-boiling throttling unit, the low-boiling evaporation unit and the low-boiling gas separation unit and returns to the air inlet end of the middle cavity of the compression unit;
the heat pump system establishes three-level heat treatment responses of drying, drying + dehumidifying and deep dehumidifying in the system through the arranged non-azeotropic mixed working medium heat exchange unit and corresponding units arranged in front of and behind the non-azeotropic mixed working medium heat exchange unit in a matching manner.
The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system is characterized by comprising the following steps of:
when the drying operation is performed,
the heat release and condensation of the gaseous low-boiling working medium are finished through a low-boiling condensing unit arranged in the non-azeotropic mixed working medium heat exchange unit, and the low-boiling working medium subjected to heat release and condensation is led to a heat return unit;
meanwhile, the high-boiling evaporation unit arranged in the non-azeotropic mixed working medium heat exchange unit completes the evaporation and heat absorption of the high-boiling working medium, and the high-boiling working medium subjected to evaporation and heat absorption is led to the heat return unit;
fresh air is made into hot air by the condensing unit and the low-boiling condensing unit and then is led to the drying area, return air formed after drying is sent to the high-boiling evaporating unit for dehumidification and cooling to form cold air, and the cold air subjected to dehumidification and cooling is led to the low-boiling condensing unit as air for heat exchange of the low-boiling condensing unit; the non-azeotropic mixed working medium heat exchange unit completes heat exchange of high-low boiling working medium based on the low-boiling condensation unit and the high-boiling evaporation unit by using the wind as a medium through the arranged wind circulation structure.
The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system is characterized by comprising the following steps of:
when the operation of deep dehumidification is carried out,
the heat exchange of the high-boiling working medium and the low-boiling working medium is completed through a self-cascade heat exchange unit arranged in the non-azeotropic mixed working medium heat exchange unit; to form condensation and subcooling of the low boiling working fluid.
The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system is characterized by comprising the following steps of:
when the drying and dehumidifying operation is carried out,
a low-boiling condensation unit, a high-boiling evaporation unit and a self-cascade heat exchange unit are arranged in the non-azeotropic mixed working medium heat exchange unit;
the gas outlet of the gas separation unit is connected with the inlet of the low-boiling condensation unit and the low-boiling working medium inlet of the self-cascade heat exchange unit through a first three-way proportional valve;
the outlet of the high-boiling throttling unit is connected with the inlet of the high-boiling evaporation unit and the high-boiling working medium inlet of the self-cascade heat exchange unit through a second three-way proportional valve;
the outlet of the low-boiling condensing unit and the low-boiling working medium outlet of the self-cascade heat exchange unit are connected with the low-boiling working medium inlet of the heat regeneration unit through a third three-way proportional valve;
the outlet of the high-boiling evaporation unit and the high-boiling working medium outlet of the self-cascade heat exchange unit are connected with the high-boiling working medium inlet of the heat regeneration unit through a fourth three-way proportional valve;
the low-boiling working medium entering the low-boiling condensing unit and the self-cascade heat exchange unit is subjected to proportion regulation through a first three-way proportional valve;
the high-boiling working medium entering the high-boiling evaporation unit and the self-cascade heat exchange unit is subjected to proportion regulation through a second three-way proportional valve;
the heat release liquefaction of the gaseous low-boiling working medium is finished through the low-boiling condensing unit, and the low-boiling working medium subjected to the heat release liquefaction is led to the heat recovery unit; meanwhile, the high-boiling evaporation unit completes the gasification and heat absorption of the high-boiling working medium, and the high-boiling working medium subjected to the gasification and heat absorption is led to the heat regeneration unit;
the fresh air is made into hot air by the low-boiling condensation unit and the high-boiling condensation unit and then is led to the drying area, return air formed after drying is sent to the high-boiling evaporation unit for dehumidification and cooling to form cold air, and the cold air subjected to dehumidification and cooling is led to the low-boiling condensation unit as air for heat exchange of the low-boiling condensation unit; the non-azeotropic mixed working medium heat exchange unit completes heat exchange of high-low boiling working medium based on the low-boiling condensation unit and the high-boiling evaporation unit by using the wind as a medium through the arranged wind circulation structure;
meanwhile, the heat exchange of the high-boiling and low-boiling working media is completed through the self-cascade heat exchange unit; to form condensation and subcooling of the low boiling working fluid.
The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system is characterized by comprising the following steps of:
the drying and dehumidifying method is characterized in that the drying, dehumidifying and deep dehumidifying three-level heat treatment responses are matched through an established air circulation system;
the preparation of hot air for drying is finished through a condensing unit;
drying the area to be dried to form dried return air;
cold air is produced by the low-boiling evaporation unit to form inlet air for heat exchange of the condensation unit;
the air outlet end of the condensation unit → the air inlet end of the drying area → the air return end after drying → the air inlet end of the condensation unit to form a first air circulation loop;
the air outlet end of the condensation unit → the air inlet end of the drying area → the air return end after drying → the air inlet end of the low-boiling evaporation unit → the air inlet end of the condensation unit to form a second air circulation loop;
when the drying operation is carried out, the first air circulation loop is taken as the main part, and the second air circulation loop is taken as the auxiliary part;
when drying and dehumidifying are operated, the first air circulation loop is taken as an auxiliary loop, and the second air circulation loop is taken as a main loop;
when deep dehumidification is performed, only the second wind circulation loop is started.
The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system is characterized by comprising the following steps of:
the drying and dehumidifying method is characterized in that the drying, dehumidifying and deep dehumidifying three-level heat treatment responses are matched through an established air circulation system;
the preparation of hot air for drying is finished through a condensing unit;
drying the area to be dried to form dried return air;
cold air is produced by the low-boiling evaporation unit to form inlet air for heat exchange of the condensation unit;
the air outlet end of the condensation unit → the air inlet end of the drying area → the air return end after drying → the air inlet end of the condensation unit to form a first air circulation loop;
the air outlet end of the condensation unit → the air inlet end of the drying area → the air return end after drying → the air inlet end of the low-boiling evaporation unit → the air inlet end of the condensation unit to form a second air circulation loop;
when the drying operation is carried out, the first air circulation loop is taken as the main part, and the second air circulation loop is taken as the auxiliary part;
when drying and dehumidifying are operated, the first air circulation loop is taken as an auxiliary loop, and the second air circulation loop is taken as a main loop;
when deep dehumidification is performed, only the second wind circulation loop is started.
The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system is characterized by comprising the following steps of:
when the drying is operated, the drying machine is operated,
the mixed working medium discharged from the exhaust end of the compression unit passes through the arranged condensation unit and the gas separation unit to form gas-liquid separation of the low-boiling working medium and the high-boiling working medium;
the liquid high-boiling working medium passes through the high-boiling throttling unit, then is led to the high-boiling evaporation unit for heat absorption and gasification, and then is led to the heat regeneration unit;
gaseous low-boiling working medium passes through the low-boiling condensing unit and then is led to the heat recovery unit, and the gaseous low-boiling working medium and the high-boiling working medium led to the heat recovery unit complete heat exchange;
the high-boiling working medium which completes heat exchange through the heat recovery unit returns to the air suction end of the compression unit, and the low-boiling working medium which completes heat exchange through the heat recovery unit sequentially passes through the low-boiling throttling unit, the low-boiling evaporation unit and the low-boiling gas sub-unit and returns to the air inlet end of the middle cavity of the compression unit.
The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system is characterized by comprising the following steps of:
when the drying and the dehumidification are operated,
the mixed working medium discharged from the exhaust end of the compression unit passes through the arranged condensation unit and the gas separation unit to form gas-liquid separation of the low-boiling working medium and the high-boiling working medium;
after passing through the high-boiling throttling unit, the liquid high-boiling working medium is respectively led to the high-boiling evaporation unit through a second three-way proportional valve to perform heat absorption and gasification, led to the self-cascade heat exchange unit to perform heat exchange, and then led to the heat regeneration unit in a unified way;
gaseous low-boiling working media are respectively led to the low-boiling condensing unit and the self-cascade heat exchange unit through the first three-way proportional valve, then are led to the heat recovery unit in a unified mode, and finish heat exchange with high-boiling working media led to the heat recovery unit;
the high-boiling working medium which completes heat exchange through the heat recovery unit returns to the air suction end of the compression unit, and the low-boiling working medium which completes heat exchange through the heat recovery unit sequentially passes through the low-boiling throttling unit, the low-boiling evaporation unit and the low-boiling gas sub-unit and returns to the air inlet end of the middle cavity of the compression unit.
The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system is characterized by comprising the following steps of:
when the operation is carried out with deep dehumidification,
the mixed working medium discharged from the exhaust end of the compression unit passes through the arranged condensation unit and the gas separation unit to form gas-liquid separation of the low-boiling working medium and the high-boiling working medium;
after the self-cascade heat exchange unit finishes the first heat exchange, the liquid high-boiling working medium is respectively led to the heat recovery unit;
the high-boiling working medium which completes heat exchange through the heat recovery unit returns to the air suction end of the compression unit, and the low-boiling working medium which completes heat exchange through the heat recovery unit sequentially passes through the low-boiling throttling unit, the low-boiling evaporation unit and the low-boiling gas sub-unit and returns to the air inlet end of the middle cavity of the compression unit.
The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system is characterized by comprising the following steps of:
the first air circulation loop and the second air circulation loop are adjusted or switched in proportion through an air channel switching valve.
The invention relates to a drying and dehumidifying method based on a non-azeotropic mixed working medium heat pump system,
the threshold limit of the conventional dew point of the evaporator can be broken through, and deep dehumidification is formed;
separate responses to temperature heating and dehumidification, or sequential responses, may be established;
a non-azeotropic refrigerant is adopted, and an air injection enthalpy-increasing structure is introduced, so that a low-boiling refrigerant is introduced into an intermediate pressure cavity of a compression unit, and the effects of supplementing air and reducing energy consumption are achieved;
the adjustment of the high, medium and low air supply temperature required by the drying and dehumidifying material at different periods can be realized by changing the opening degree of an air valve in the air system; in addition, by the arranged non-azeotropic mixed working medium heat exchange unit structure, quick drying and dehumidification can be realized in the early stage of dehumidification; in the middle stage of dehumidification, the proportion type response of drying and dehumidification can be carried out through the internal structure of the arranged non-azeotropic mixed working medium heat exchange unit; and in the later stage of dehumidification, according to the self-overlapping operation rule, water molecules in the low-humidity air flow entering the dehumidification section are directly desublimated, so that efficient deep drying and dehumidification of the material are realized.
Drawings
FIG. 1 is a block diagram schematically illustrating the structure of the present invention;
FIG. 2 is a schematic diagram of the internal structure of a non-azeotropic mixed working medium heat exchange unit in the present invention;
FIG. 3 is a schematic block diagram of the structure of the wind circulation system of the present invention;
FIG. 4 is a schematic diagram of a heat pump system according to an embodiment of the present invention;
FIG. 5 is a schematic view of an embodiment of a wind turbine system;
FIG. 6 is a schematic diagram illustrating the operation of the heat pump system at stage one according to an embodiment of the present invention;
FIG. 7 is a schematic diagram of the operation of the heat pump system corresponding to stage two in the embodiment of the present invention;
fig. 8 is a schematic diagram of the operation of the heat pump system corresponding to stage three in the embodiment of the present invention.
Detailed Description
The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system according to the present invention will be further specifically described with reference to the drawings and the detailed description thereof.
As shown in figures 1, 2 and 4, a drying and dehumidifying method based on a non-azeotropic mixed working medium heat pump system,
in the heat pump system, the mixed working medium discharged from the exhaust end of the compression unit passes through the arranged condensation unit and the gas separation unit to form gas-liquid separation of the low-boiling working medium and the high-boiling working medium;
after passing through the high-boiling throttling unit, the liquid high-boiling working medium leads to the non-azeotropic mixed working medium heat exchange unit and carries out first heat exchange with the gaseous low-boiling working medium leading to the non-azeotropic mixed working medium heat exchange unit, and then leads to the regenerative unit for carrying out second heat exchange of the high-boiling working medium and the low-boiling working medium;
the high-boiling working medium which completes the second heat exchange returns to the air suction end of the compression unit, and the low-boiling working medium which completes the second heat exchange sequentially passes through the low-boiling throttling unit, the low-boiling evaporation unit and the low-boiling gas separation unit and returns to the air inlet end of the middle cavity of the compression unit;
the heat pump system establishes three-level heat treatment responses of drying, drying + dehumidifying and deep dehumidifying in the system through the arranged non-azeotropic mixed working medium heat exchange unit and corresponding units arranged in front of and behind the non-azeotropic mixed working medium heat exchange unit in a matching manner.
Wherein,
when the drying operation is performed,
the heat release and condensation of the gaseous low-boiling working medium are finished through a low-boiling condensing unit arranged in the non-azeotropic mixed working medium heat exchange unit, and the low-boiling working medium subjected to heat release and condensation is led to a heat return unit;
meanwhile, the high-boiling evaporation unit arranged in the non-azeotropic mixed working medium heat exchange unit completes the evaporation and heat absorption of the high-boiling working medium, and the high-boiling working medium subjected to evaporation and heat absorption is led to the heat return unit;
fresh air is made into hot air by the condensing unit and the low-boiling condensing unit and then is led to the drying area, return air formed after drying is sent to the high-boiling evaporating unit for dehumidification and cooling to form cold air, and the cold air subjected to dehumidification and cooling is led to the low-boiling condensing unit as air for heat exchange of the low-boiling condensing unit; the non-azeotropic mixed working medium heat exchange unit completes heat exchange of high-low boiling working medium based on the low-boiling condensation unit and the high-boiling evaporation unit by using the wind as a medium through the arranged wind circulation structure.
Wherein,
when the operation of deep dehumidification is carried out,
the heat exchange of the high-boiling working medium and the low-boiling working medium is completed through a self-cascade heat exchange unit arranged in the non-azeotropic mixed working medium heat exchange unit; to form condensation and subcooling of the low boiling working fluid.
Wherein,
when the drying and dehumidifying operation is carried out,
a low-boiling condensation unit, a high-boiling evaporation unit and a self-cascade heat exchange unit are arranged in the non-azeotropic mixed working medium heat exchange unit;
the gas outlet of the gas separation unit is connected with the inlet of the low-boiling condensation unit and the low-boiling working medium inlet of the self-cascade heat exchange unit through a first three-way proportional valve;
the outlet of the high-boiling throttling unit is connected with the inlet of the high-boiling evaporation unit and the high-boiling working medium inlet of the self-cascade heat exchange unit through a second three-way proportional valve;
the outlet of the low-boiling condensing unit and the low-boiling working medium outlet of the self-cascade heat exchange unit are connected with the low-boiling working medium inlet of the heat regeneration unit through a third three-way proportional valve;
the outlet of the high-boiling evaporation unit and the high-boiling working medium outlet of the self-cascade heat exchange unit are connected with the high-boiling working medium inlet of the heat regeneration unit through a fourth three-way proportional valve;
the low-boiling working medium entering the low-boiling condensing unit and the self-cascade heat exchange unit is subjected to proportion regulation through a first three-way proportional valve;
the high-boiling working medium entering the high-boiling evaporation unit and the self-cascade heat exchange unit is subjected to proportion regulation through a second three-way proportional valve;
the heat release liquefaction of the gaseous low-boiling working medium is finished through the low-boiling condensing unit, and the low-boiling working medium subjected to the heat release liquefaction is led to the heat recovery unit; meanwhile, the high-boiling evaporation unit completes the gasification and heat absorption of the high-boiling working medium, and the high-boiling working medium subjected to the gasification and heat absorption is led to the heat regeneration unit;
the fresh air is made into hot air by the low-boiling condensation unit and the high-boiling condensation unit and then is led to the drying area, return air formed after drying is sent to the high-boiling evaporation unit for dehumidification and cooling to form cold air, and the cold air subjected to dehumidification and cooling is led to the low-boiling condensation unit as air for heat exchange of the low-boiling condensation unit; the non-azeotropic mixed working medium heat exchange unit completes heat exchange of high-low boiling working medium based on the low-boiling condensation unit and the high-boiling evaporation unit by using the wind as a medium through the arranged wind circulation structure;
meanwhile, the heat exchange of the high-boiling and low-boiling working media is completed through the self-cascade heat exchange unit; to form condensation and subcooling of the low boiling working fluid.
In which, as shown in figure 3,
the drying and dehumidifying method is characterized in that the drying, dehumidifying and deep dehumidifying three-level heat treatment responses are matched through an established air circulation system;
the preparation of hot air for drying is finished through a condensing unit;
drying the area to be dried to form dried return air;
cold air is produced by the low-boiling evaporation unit to form inlet air for heat exchange of the condensation unit;
the air outlet end of the condensation unit → the air inlet end of the drying area → the air return end after drying → the air inlet end of the condensation unit to form a first air circulation loop;
the air outlet end of the condensation unit → the air inlet end of the drying area → the air return end after drying → the air inlet end of the low-boiling evaporation unit → the air inlet end of the condensation unit to form a second air circulation loop;
when the drying operation is carried out, the first air circulation loop is taken as the main part, and the second air circulation loop is taken as the auxiliary part;
when drying and dehumidifying are operated, the first air circulation loop is taken as an auxiliary loop, and the second air circulation loop is taken as a main loop;
when deep dehumidification is performed, only the second wind circulation loop is started.
Wherein,
the drying and dehumidifying method is characterized in that the drying, dehumidifying and deep dehumidifying three-level heat treatment responses are matched through an established air circulation system;
the preparation of hot air for drying is finished through a condensing unit;
drying the area to be dried to form dried return air;
cold air is produced by the low-boiling evaporation unit to form inlet air for heat exchange of the condensation unit;
the air outlet end of the condensation unit → the air inlet end of the drying area → the air return end after drying → the air inlet end of the condensation unit to form a first air circulation loop;
the air outlet end of the condensation unit → the air inlet end of the drying area → the air return end after drying → the air inlet end of the low-boiling evaporation unit → the air inlet end of the condensation unit to form a second air circulation loop;
when the drying operation is carried out, the first air circulation loop is taken as the main part, and the second air circulation loop is taken as the auxiliary part;
when drying and dehumidifying are operated, the first air circulation loop is taken as an auxiliary loop, and the second air circulation loop is taken as a main loop;
when deep dehumidification is performed, only the second wind circulation loop is started.
Wherein,
when the drying is operated, the drying machine is operated,
the mixed working medium discharged from the exhaust end of the compression unit passes through the arranged condensation unit and the gas separation unit to form gas-liquid separation of the low-boiling working medium and the high-boiling working medium;
the liquid high-boiling working medium passes through the high-boiling throttling unit, then is led to the high-boiling evaporation unit for heat absorption and gasification, and then is led to the heat regeneration unit;
gaseous low-boiling working medium passes through the low-boiling condensing unit and then is led to the heat recovery unit, and the gaseous low-boiling working medium and the high-boiling working medium led to the heat recovery unit complete heat exchange;
the high-boiling working medium which completes heat exchange through the heat recovery unit returns to the air suction end of the compression unit, and the low-boiling working medium which completes heat exchange through the heat recovery unit sequentially passes through the low-boiling throttling unit, the low-boiling evaporation unit and the low-boiling gas sub-unit and returns to the air inlet end of the middle cavity of the compression unit.
Wherein,
when the drying and the dehumidification are operated,
the mixed working medium discharged from the exhaust end of the compression unit passes through the arranged condensation unit and the gas separation unit to form gas-liquid separation of the low-boiling working medium and the high-boiling working medium;
after passing through the high-boiling throttling unit, the liquid high-boiling working medium is respectively led to the high-boiling evaporation unit through a second three-way proportional valve to perform heat absorption and gasification, led to the self-cascade heat exchange unit to perform heat exchange, and then led to the heat regeneration unit in a unified way;
gaseous low-boiling working media are respectively led to the low-boiling condensing unit and the self-cascade heat exchange unit through the first three-way proportional valve, then are led to the heat recovery unit in a unified mode, and finish heat exchange with high-boiling working media led to the heat recovery unit;
the high-boiling working medium which completes heat exchange through the heat recovery unit returns to the air suction end of the compression unit, and the low-boiling working medium which completes heat exchange through the heat recovery unit sequentially passes through the low-boiling throttling unit, the low-boiling evaporation unit and the low-boiling gas sub-unit and returns to the air inlet end of the middle cavity of the compression unit.
Wherein,
when the operation is carried out with deep dehumidification,
the mixed working medium discharged from the exhaust end of the compression unit passes through the arranged condensation unit and the gas separation unit to form gas-liquid separation of the low-boiling working medium and the high-boiling working medium;
after the self-cascade heat exchange unit finishes the first heat exchange, the liquid high-boiling working medium is respectively led to the heat recovery unit;
the high-boiling working medium which completes heat exchange through the heat recovery unit returns to the air suction end of the compression unit, and the low-boiling working medium which completes heat exchange through the heat recovery unit sequentially passes through the low-boiling throttling unit, the low-boiling evaporation unit and the low-boiling gas sub-unit and returns to the air inlet end of the middle cavity of the compression unit.
Wherein,
the first air circulation loop and the second air circulation loop are adjusted or switched in proportion through an air channel switching valve.
Working principle and embodiment
The inverter compressor 1 in the present embodiment corresponds to the compression unit described above;
the first condenser 2 in the present embodiment corresponds to the above-described condensing unit;
the liquid storage type air separator 3 in the present embodiment corresponds to the air separation unit described above;
the first electronic expansion valve 4 in the present embodiment corresponds to the high-boiling throttle unit described above;
the first evaporator 5 in the present embodiment corresponds to the high-boiling evaporation unit described above;
the heat regenerator 6 in the present embodiment corresponds to the heat regenerating unit described above;
the second condenser 7 in the present embodiment corresponds to the low-boiling condensation unit described above;
the second electronic expansion valve 8 in the present embodiment corresponds to the low-boiling throttle unit described above;
the second evaporator 9 in the present embodiment corresponds to the low-boiling evaporation unit described above;
the gas-liquid separator 10 in the present embodiment corresponds to the low-boiling gas separation unit described above;
the self-cascade heat exchanger 12 in this embodiment corresponds to the self-cascade heat exchange unit described above;
the three-way electromagnetic valve 11 in this embodiment corresponds to the first three-way proportional valve, the second three-way proportional valve, the third three-way proportional valve, and the fourth three-way proportional valve.
Stage one: early stage of dehumidification (relative humidity in system 70-100%)
The system operates: a quasi-self-cascade run, as shown in FIG. 6;
the refrigerant after being compressed circulates to the first condenser 2 after the compressor 1 is started, the refrigerant gas which is not condensed enters the second condenser 7 after passing through the liquid storage type gas separator 3 to be condensed into refrigerant liquid, then enters the economizer (heat regenerator) 6 again for heat exchange, then is throttled by the second electronic expansion valve 8, enters the second evaporator 9 for evaporation and heat absorption, and finally enters the middle cavity of the compressor 1; and the high-boiling refrigerant passes through the liquid storage type air separator 3, enters the first evaporator 5 for evaporation and heat absorption after the throttling action of the first electronic expansion valve 4, and finally returns to the air suction end of the compressor 1. The wind respectively passes through the second condenser 7 and the first condenser 2 to reach the temperature of about 65 ℃, and then is dehumidified by the second evaporator 9 and the first evaporator 5, and partial water vapor in the air is directly desublimated. The air valve 12 in the air duct system opens most of the hot air (A) and directly returns the materials through the air valve, thus achieving the purpose of continuously heating and warming, and a small part of the air (B) enters the second evaporator 9 and the first evaporator 5 for a small amount of dehumidification. The main purpose of this stage is to evaporate the moisture in the material into the wind system. At this point, the material moisture is volatilized, the moisture content of the moisture in the air system is gradually increased, and the frequency of the compressor is increased until the maximum 65HZ is reached.
And a second stage: middle stage of dehumidification (relative humidity in system 30-69%)
The system is operated; self-recovery operation and class overlapping operation; as shown in fig. 7;
the refrigerant after being compressed after the compressor 1 is started circulates to the first condenser 2, and the refrigerant gas which is not condensed passes through the liquid storage type gas separator 3; through the adjustment of the three-way proportional valve 11, a part of the refrigerant enters the self-cascade heat exchanger 12 and is condensed into refrigerant liquid, and then the refrigerant liquid enters the economizer again for heat exchange; the other part of the refrigerant enters a second condenser 7 to be condensed into refrigerant liquid, and then enters an economizer (a heat regenerator) 6 again for heat exchange; after heat exchange is completed by the heat regenerator, the heat is throttled by the second electronic expansion valve 8, enters the second evaporator 9 for evaporation and heat absorption, and finally enters the middle cavity of the compressor 1; after passing through the liquid storage type gas separator 3, the high-boiling refrigerant passes through the throttling action of the first electronic expansion valve 4, one part of the high-boiling refrigerant enters the self-cascade heat exchanger 12 through the three-way proportional valve 11, the other part of the high-boiling refrigerant enters the first evaporator 5, the high-boiling refrigerant passing through the self-cascade heat exchanger 12 and the first evaporator 5 simultaneously enters the heat regenerator for heat exchange, and the high-boiling refrigerant gas after heat exchange is finished by the heat regenerator 6 returns to the air suction end of the compressor. At which time the compressor remains in the initial low frequency operation of 50 HZ. The wind respectively passes through the second condenser 7 and the first condenser 2, reaches the temperature of about 55 ℃, then passes through the second evaporator 9 and the first evaporator 5 for deep dehumidification, and the water vapor in the air is directly desublimated. The air valve 12 in the air duct system opens a small part of hot air (A) to directly return the material through the air valve, so that the aim of drying the residual moisture of the material is fulfilled, and a large part of air (B) enters the second evaporator and the first evaporator to be partially dehumidified. When the moisture content of the water in the wind system gradually increases to a maximum, it starts to decrease the frequency until it reaches a minimum of 50 HZ.
And a third stage: the later stage of dehumidification (relative humidity in the system is 1-29%)
The system operates: self-recovery operation; as shown in fig. 8;
the refrigerant after being compressed circulates to the first condenser 2 after the compressor 1 is started, the refrigerant gas which is not condensed enters the self-cascade heat exchanger 12 after passing through the liquid storage type gas separator 3 to be condensed into refrigerant liquid, then enters the economizer 6 again for heat exchange, is throttled by the second electronic expansion valve 8, enters the second evaporator 9 for evaporation and heat absorption, and finally enters the middle cavity of the compressor 1; and the high-boiling refrigerant passes through the liquid storage type gas separator 3, enters the self-cascade heat exchanger 12 after passing through the throttling action of the first electronic expansion valve 4 to complete heat exchange, enters the economizer 6 for further heat exchange, and returns the refrigerant gas after completing the heat exchange to the air suction end of the compressor. At which time the compressor remains operating at a low frequency of 45 HZ. After the wind passes through the first condenser 2 and reaches the temperature of about 50 ℃, the wind is deeply dehumidified by the second evaporator and the first evaporator, and the water vapor in the air is directly desublimated. The air valve 12 in the air duct system is completely opened, and hot air (B) directly enters the first evaporator for deep dehumidification. At the moment, the evaporation temperature in the evaporator is below zero, and water vapor in wind is directly desublimated, so that the purpose of deep dehumidification is achieved.
The invention relates to a drying and dehumidifying method based on a non-azeotropic mixed working medium heat pump system,
the threshold limit of the conventional dew point of the evaporator can be broken through, and deep dehumidification is formed;
separate responses to temperature heating and dehumidification, or sequential responses, may be established;
a non-azeotropic refrigerant is adopted, a structure for increasing the enthalpy of air injection is introduced, and a low-boiling refrigerant is introduced into an intermediate pressure cavity of a compression unit, so that the effects of air supplement and energy consumption reduction are achieved (the same as above);
the adjustment of high, medium and low air supply temperatures required by the drying and dehumidifying materials at different periods can be realized by changing the opening degree of an air valve in an air system and combining the opening frequency of a compressor; in addition, by the arranged non-azeotropic mixed working medium heat exchange unit structure, quick drying and dehumidification can be realized in the early stage of dehumidification; according to the self-overlapping operation rule, the water molecules in the low-humidity air flow entering the dehumidification section are directly desublimated, so that the efficient deep drying and dehumidification of the materials are realized; in the middle stage of dehumidification, the proportion type response of drying and dehumidification can be carried out through the internal structure of the arranged non-azeotropic mixed working medium heat exchange unit.
Claims (10)
1. A drying and dehumidifying method based on a non-azeotropic mixed working medium heat pump system is characterized in that:
in the heat pump system, the mixed working medium discharged from the exhaust end of the compression unit passes through the arranged condensation unit and the gas separation unit to form gas-liquid separation of the low-boiling working medium and the high-boiling working medium;
after passing through the high-boiling throttling unit, the liquid high-boiling working medium leads to the non-azeotropic mixed working medium heat exchange unit and carries out first heat exchange with the gaseous low-boiling working medium leading to the non-azeotropic mixed working medium heat exchange unit, and then leads to the regenerative unit for carrying out second heat exchange of the high-boiling working medium and the low-boiling working medium;
the high-boiling working medium which completes the second heat exchange returns to the air suction end of the compression unit, and the low-boiling working medium which completes the second heat exchange sequentially passes through the low-boiling throttling unit, the low-boiling evaporation unit and the low-boiling gas separation unit and returns to the air inlet end of the middle cavity of the compression unit;
the heat pump system establishes three-level heat treatment responses of drying, drying + dehumidifying and deep dehumidifying in the system through the arranged non-azeotropic mixed working medium heat exchange unit and corresponding units arranged in front of and behind the non-azeotropic mixed working medium heat exchange unit in a matching manner.
2. The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system according to claim 1, wherein:
when the drying operation is performed,
the heat release and condensation of the gaseous low-boiling working medium are finished through a low-boiling condensing unit arranged in the non-azeotropic mixed working medium heat exchange unit, and the low-boiling working medium subjected to heat release and condensation is led to a heat return unit;
meanwhile, the high-boiling evaporation unit arranged in the non-azeotropic mixed working medium heat exchange unit completes the evaporation and heat absorption of the high-boiling working medium, and the high-boiling working medium subjected to evaporation and heat absorption is led to the heat return unit;
fresh air is made into hot air by the condensing unit and the low-boiling condensing unit and then is led to the drying area, return air formed after drying is sent to the high-boiling evaporating unit for dehumidification and cooling to form cold air, and the cold air subjected to dehumidification and cooling is led to the low-boiling condensing unit as air for heat exchange of the low-boiling condensing unit; the non-azeotropic mixed working medium heat exchange unit completes heat exchange of high-low boiling working medium based on the low-boiling condensation unit and the high-boiling evaporation unit by using the wind as a medium through the arranged wind circulation structure.
3. The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system according to claim 1, wherein:
when the operation of deep dehumidification is carried out,
the heat exchange of the high-boiling working medium and the low-boiling working medium is completed through a self-cascade heat exchange unit arranged in the non-azeotropic mixed working medium heat exchange unit; to form condensation and subcooling of the low boiling working fluid.
4. The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system according to claim 1, wherein:
when the drying and dehumidifying operation is carried out,
a low-boiling condensation unit, a high-boiling evaporation unit and a self-cascade heat exchange unit are arranged in the non-azeotropic mixed working medium heat exchange unit;
the gas outlet of the gas separation unit is connected with the inlet of the low-boiling condensation unit and the low-boiling working medium inlet of the self-cascade heat exchange unit through a first three-way proportional valve;
the outlet of the high-boiling throttling unit is connected with the inlet of the high-boiling evaporation unit and the high-boiling working medium inlet of the self-cascade heat exchange unit through a second three-way proportional valve;
the outlet of the low-boiling condensing unit and the low-boiling working medium outlet of the self-cascade heat exchange unit are connected with the low-boiling working medium inlet of the heat regeneration unit through a third three-way proportional valve;
the outlet of the high-boiling evaporation unit and the high-boiling working medium outlet of the self-cascade heat exchange unit are connected with the high-boiling working medium inlet of the heat regeneration unit through a fourth three-way proportional valve;
the low-boiling working medium entering the low-boiling condensing unit and the self-cascade heat exchange unit is subjected to proportion regulation through a first three-way proportional valve;
the high-boiling working medium entering the high-boiling evaporation unit and the self-cascade heat exchange unit is subjected to proportion regulation through a second three-way proportional valve;
the heat release liquefaction of the gaseous low-boiling working medium is finished through the low-boiling condensing unit, and the low-boiling working medium subjected to the heat release liquefaction is led to the heat recovery unit; meanwhile, the high-boiling evaporation unit completes the gasification and heat absorption of the high-boiling working medium, and the high-boiling working medium subjected to the gasification and heat absorption is led to the heat regeneration unit;
the fresh air is made into hot air by the low-boiling condensation unit and the high-boiling condensation unit and then is led to the drying area, return air formed after drying is sent to the high-boiling evaporation unit for dehumidification and cooling to form cold air, and the cold air subjected to dehumidification and cooling is led to the low-boiling condensation unit as air for heat exchange of the low-boiling condensation unit; the non-azeotropic mixed working medium heat exchange unit completes heat exchange of high-low boiling working medium based on the low-boiling condensation unit and the high-boiling evaporation unit by using the wind as a medium through the arranged wind circulation structure;
meanwhile, the heat exchange of the high-boiling and low-boiling working media is completed through the self-cascade heat exchange unit; to form condensation and subcooling of the low boiling working fluid.
5. The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system according to claim 1, wherein:
the drying and dehumidifying method is characterized in that the drying, dehumidifying and deep dehumidifying three-level heat treatment responses are matched through an established air circulation system;
the preparation of hot air for drying is finished through a condensing unit;
drying the area to be dried to form dried return air;
cold air is produced by the low-boiling evaporation unit to form inlet air for heat exchange of the condensation unit;
the air outlet end of the condensation unit → the air inlet end of the drying area → the air return end after drying → the air inlet end of the condensation unit to form a first air circulation loop;
the air outlet end of the condensation unit → the air inlet end of the drying area → the air return end after drying → the air inlet end of the low-boiling evaporation unit → the air inlet end of the condensation unit to form a second air circulation loop;
when the drying operation is carried out, the first air circulation loop is taken as the main part, and the second air circulation loop is taken as the auxiliary part;
when drying and dehumidifying are operated, the first air circulation loop is taken as an auxiliary loop, and the second air circulation loop is taken as a main loop;
when deep dehumidification is performed, only the second wind circulation loop is started.
6. The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system according to claim 4, wherein:
the drying and dehumidifying method is characterized in that the drying, dehumidifying and deep dehumidifying three-level heat treatment responses are matched through an established air circulation system;
the preparation of hot air for drying is finished through a condensing unit;
drying the area to be dried to form dried return air;
cold air is produced by the low-boiling evaporation unit to form inlet air for heat exchange of the condensation unit;
the air outlet end of the condensation unit → the air inlet end of the drying area → the air return end after drying → the air inlet end of the condensation unit to form a first air circulation loop;
the air outlet end of the condensation unit → the air inlet end of the drying area → the air return end after drying → the air inlet end of the low-boiling evaporation unit → the air inlet end of the condensation unit to form a second air circulation loop;
when the drying operation is carried out, the first air circulation loop is taken as the main part, and the second air circulation loop is taken as the auxiliary part;
when drying and dehumidifying are operated, the first air circulation loop is taken as an auxiliary loop, and the second air circulation loop is taken as a main loop;
when deep dehumidification is performed, only the second wind circulation loop is started.
7. The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system according to claim 6, wherein:
when the drying is operated, the drying machine is operated,
the mixed working medium discharged from the exhaust end of the compression unit passes through the arranged condensation unit and the gas separation unit to form gas-liquid separation of the low-boiling working medium and the high-boiling working medium;
the liquid high-boiling working medium passes through the high-boiling throttling unit, then is led to the high-boiling evaporation unit for heat absorption and gasification, and then is led to the heat regeneration unit;
gaseous low-boiling working medium passes through the low-boiling condensing unit and then is led to the heat recovery unit, and the gaseous low-boiling working medium and the high-boiling working medium led to the heat recovery unit complete heat exchange;
the high-boiling working medium which completes heat exchange through the heat recovery unit returns to the air suction end of the compression unit, and the low-boiling working medium which completes heat exchange through the heat recovery unit sequentially passes through the low-boiling throttling unit, the low-boiling evaporation unit and the low-boiling gas sub-unit and returns to the air inlet end of the middle cavity of the compression unit.
8. The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system according to claim 6, wherein:
when the drying and the dehumidification are operated,
the mixed working medium discharged from the exhaust end of the compression unit passes through the arranged condensation unit and the gas separation unit to form gas-liquid separation of the low-boiling working medium and the high-boiling working medium;
after passing through the high-boiling throttling unit, the liquid high-boiling working medium is respectively led to the high-boiling evaporation unit through a second three-way proportional valve to perform heat absorption and gasification, led to the self-cascade heat exchange unit to perform heat exchange, and then led to the heat regeneration unit in a unified way;
gaseous low-boiling working media are respectively led to the low-boiling condensing unit and the self-cascade heat exchange unit through the first three-way proportional valve, then are led to the heat recovery unit in a unified mode, and finish heat exchange with high-boiling working media led to the heat recovery unit;
the high-boiling working medium which completes heat exchange through the heat recovery unit returns to the air suction end of the compression unit, and the low-boiling working medium which completes heat exchange through the heat recovery unit sequentially passes through the low-boiling throttling unit, the low-boiling evaporation unit and the low-boiling gas sub-unit and returns to the air inlet end of the middle cavity of the compression unit.
9. The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system according to claim 6, wherein:
when the operation is carried out with deep dehumidification,
the mixed working medium discharged from the exhaust end of the compression unit passes through the arranged condensation unit and the gas separation unit to form gas-liquid separation of the low-boiling working medium and the high-boiling working medium;
after the self-cascade heat exchange unit finishes the first heat exchange, the liquid high-boiling working medium is respectively led to the heat recovery unit;
the high-boiling working medium which completes heat exchange through the heat recovery unit returns to the air suction end of the compression unit, and the low-boiling working medium which completes heat exchange through the heat recovery unit sequentially passes through the low-boiling throttling unit, the low-boiling evaporation unit and the low-boiling gas sub-unit and returns to the air inlet end of the middle cavity of the compression unit.
10. The drying and dehumidifying method based on the non-azeotropic mixed working medium heat pump system according to claim 5 or 6, wherein:
the first air circulation loop and the second air circulation loop are adjusted or switched in proportion through an air channel switching valve.
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| CN204027279U (en) * | 2014-08-07 | 2014-12-17 | 广东芬尼克兹节能设备有限公司 | A kind of heat pump drying dehydrating unit |
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| CN110822879A (en) | 2020-02-21 |
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