CN110806038A - Control method of heat pump system for dehumidification and drying - Google Patents
Control method of heat pump system for dehumidification and drying Download PDFInfo
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- 238000001035 drying Methods 0.000 title claims abstract description 149
- 238000007791 dehumidification Methods 0.000 title claims abstract description 45
- 238000000034 method Methods 0.000 title claims abstract description 35
- 230000006835 compression Effects 0.000 claims abstract description 70
- 238000007906 compression Methods 0.000 claims abstract description 70
- 230000004044 response Effects 0.000 claims abstract description 15
- 238000010438 heat treatment Methods 0.000 claims abstract description 10
- 238000009835 boiling Methods 0.000 claims description 137
- 238000009833 condensation Methods 0.000 claims description 82
- 230000005494 condensation Effects 0.000 claims description 82
- 238000001704 evaporation Methods 0.000 claims description 69
- 230000008020 evaporation Effects 0.000 claims description 59
- 230000001172 regenerating effect Effects 0.000 claims description 32
- 230000009467 reduction Effects 0.000 claims description 15
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- 230000001105 regulatory effect Effects 0.000 claims description 10
- 238000006243 chemical reaction Methods 0.000 claims description 6
- 238000000926 separation method Methods 0.000 claims description 5
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- 238000012544 monitoring process Methods 0.000 claims description 3
- 239000003507 refrigerant Substances 0.000 description 31
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- 238000001816 cooling Methods 0.000 description 4
- 239000012530 fluid Substances 0.000 description 4
- 238000007710 freezing Methods 0.000 description 4
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- 230000009471 action Effects 0.000 description 3
- 238000002347 injection Methods 0.000 description 3
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- 230000001502 supplementing effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
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Classifications
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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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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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
- 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
- F26B21/02—Circulating air or gases in closed cycles, e.g. wholly within the drying enclosure
- F26B21/04—Circulating air or gases in closed cycles, e.g. wholly within the drying enclosure partly outside the drying enclosure
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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
- 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
Abstract
A control method of a heat pump system for dehumidification and drying is characterized in that different heat treatment responses are realized through the control of the system, the drying requirements of different stages are met, the control is established according to two factors of relative humidity and air outlet temperature of a drying area and according to different stages of drying, the drying comprises three stages of a drying early stage, a drying middle stage and a drying later stage, and a control object points to the inside of the system: working frequency of the working medium circulation loop, the wind circulation loop and the compression unit; the working frequency of the compression unit correspondingly forms an early-stage frequency, a middle-stage frequency and a later-stage frequency according to different drying stages; the invention relates to a control method of a heat pump system for dehumidification and drying, which is characterized in that identification of the stage of drying is established through monitored relative humidity and outlet air temperature; establishing response control operation of the early drying stage, the middle drying stage and the later drying stage; the threshold limit of the conventional dew point of the evaporator can be broken through while establishing separate responses, or sequential responses, to temperature heating and dehumidification, resulting in deep dehumidification.
Description
Technical Field
The invention belongs to the field of drying and dehumidifying of medicinal materials and the like, and particularly relates to a control method of a heat pump system for dehumidifying and drying.
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: 201811036483.5 discloses an ultra-high temperature non-azeotropic working medium heat pump unit, which integrates the condenser of an electric heat pump and the evaporator regenerator of an absorption heat pump into a whole, and realizes the processes of Freon condensation, solution regeneration and refrigerant evaporation at the same time. Meanwhile, a novel non-azeotropic working medium HD-01 is used in the electric heat pump, and the condensation temperature of the novel non-azeotropic working medium can reach more than 130 ℃. The ultra-high temperature non-azeotropic heat pump unit can be used for recovering industrial waste heat below 50 ℃ and heating a heated medium to above 180 ℃.
The application numbers are: 201811525426.3 discloses a vacuum freezing and drying device using non-azeotropic mixed refrigerant, which comprises a heat pump subsystem, a freezing-drying subsystem and a vacuum subsystem, wherein the heat pump subsystem comprises a refrigeration compressor, a four-way reversing valve, a condenser, a high boiling point expansion valve, an evaporative condenser, a low boiling point expansion valve, a freezing electromagnetic valve, a freezing evaporator, a condensation electromagnetic valve and a water vapor condenser, and the freezing-drying subsystem comprises a vacuum freezing and drying box, a water vapor condensation box, a vacuum valve, a shelf for products, a drain valve, a heat storage water tank, a first circulating pump, a heating medium electromagnetic valve, a drying heat exchanger, a second circulating pump and a temperature control liquid supplementing valve.
The application numbers are: 201811595434.5, discloses a novel synergistic low-temperature self-cascade refrigeration system and working process, a throttle valve is arranged behind a liquid phase outlet of a first gas-liquid separator, and a second gas-liquid separator is arranged at the outlet of the throttle valve; the high-pressure two-phase refrigerant fluid at the outlet of the condenser enters a first gas-liquid separator to be separated into a gas phase rich in low-boiling components and a liquid phase rich in high-boiling components; wherein the liquid phase fluid rich in the high boiling point component enters a second gas-liquid separator after being throttled by a throttle valve to be separated into a gas phase and a liquid phase; in the second gas-liquid separator, the low-boiling point working medium is separated again in a gas phase and is mixed with the refrigerant at the gas phase outlet of the first gas-liquid separator to form a refrigerant fluid with higher low-boiling point components, and the refrigerant fluid is condensed by the evaporation condenser and throttled by the throttle valve and then enters the evaporator to absorb heat.
The application numbers are: 201811596700.6 discloses a 'vapor-injection enthalpy-increasing heat pump circulation system with a subcooler by adopting a non-azeotropic mixture', a compressor is connected with a condenser, the outlet of the condenser is divided into two paths, one path is connected with a second subcooler by a first subcooler and a first expansion valve, and then is connected with a middle air jet of the compressor by the first subcooler; the other path is connected with the inlet of the second expansion valve through a second subcooler and a third subcooler, the outlet of the second expansion valve is connected with the inlet of the evaporator, and the outlet of the evaporator is connected with the low-pressure inlet of the compressor through the third subcooler.
Disclosure of Invention
In order to solve the above problems, the present invention provides a control method of a heat pump system for dehumidification drying, the technical scheme is as follows:
a control method of a heat pump system for dehumidification and drying realizes different heat treatment responses by controlling the system and meets the drying requirements of different stages, and is characterized in that:
the control is established according to two factors of the relative humidity and the outlet air temperature of the drying area and according to different drying stages,
the different stages of drying include: in the early stage of drying, in the middle stage of drying and in the later stage of drying,
the control object points to the following settings in the system: working frequency of the working medium circulation loop, the wind circulation loop and the compression unit;
the working medium is a non-azeotropic mixed working medium, and the working medium circulation loop comprises: the system comprises a first high-boiling working medium circulation loop, a first low-boiling working medium circulation loop, a second high-boiling working medium circulation loop and a second low-boiling working medium circulation loop;
the wind circulation loop comprises: a first wind circulation loop and a second wind circulation loop;
the working frequency of the compression unit is established according to the early drying stage, the middle drying stage and the later drying stage, and the early stage frequency, the middle stage frequency and the later stage frequency are correspondingly formed;
the control method of the heat pump system for dehumidification and drying establishes identification of the drying stage through real-time monitoring of relative humidity and outlet air temperature; by operating the early-stage frequency, operating a first high-boiling working medium circulation loop to be matched with a first low-boiling working medium circulation loop, and combining with wind circulation based on the first wind circulation loop as a main part and a second wind circulation loop as an auxiliary part to respond to the early stage of drying; by operating the middle-term frequency, operating a first high/low boiling working medium circulation loop and a second high/low boiling working medium circulation loop, and combining with the wind circulation taking the first wind circulation loop as the auxiliary based on the second wind circulation loop as the main part to respond to the middle-term drying; and through the operation of later-period frequency, the second high-boiling working medium circulation loop is operated to be matched with the second low-boiling working medium circulation loop, and then the wind circulation based on the second wind circulation loop is combined to respond to the later drying period.
2. The control method of the heat pump system for dehumidifying and drying according to claim 1, wherein:
the first high-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the first throttling end, the first evaporation end and the heat regenerative heat exchange end of the compression unit in sequence;
the first low-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the second condensation end, the heat regenerative heat exchange end, the second throttling end, the second evaporation end and the second air distribution end of the compression unit in sequence;
the second high-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the first throttling end, the self-cascade heat exchange end and the regenerative heat exchange end of the compression unit in sequence;
the second low-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the self-cascade heat exchange end, the second throttling end, the second evaporation end and the second air distribution end of the compression unit in sequence;
the first air circulation loop is communicated to the drying area through an air outlet of the condensing end and then returns to an air inlet of the condensing end from an air return end of the drying area;
the second air circulation loop is communicated to the drying area through an air outlet of the condensing end, then communicated to an air inlet of the evaporating end from an air return end of the drying area, and then communicated to an air inlet of the condensing end from an air outlet of the evaporating end;
and a proportion regulating valve is arranged at the air return end of the drying area and used for regulating the independent operation or the proportion operation of the first air circulation loop and the second air circulation loop.
3. The control method of the heat pump system for dehumidifying and drying according to claim 1, wherein:
the first high-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the first throttling end, the first evaporation end and the heat regenerative heat exchange end of the compression unit in sequence;
the first low-boiling working medium circulation loop returns to the gas inlet end of the middle cavity of the compression unit through the gas exhaust end, the first condensation end, the first gas branch end, the second condensation end, the heat regenerative heat exchange end, the second throttling end, the second evaporation end and the second gas branch end of the compression unit in sequence;
the second high-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the first throttling end, the self-cascade heat exchange end and the regenerative heat exchange end of the compression unit in sequence;
the second low-boiling working medium circulation loop returns to the gas inlet end of the middle cavity of the compression unit through the gas exhaust end, the first condensation end, the first gas distribution end, the self-cascade heat exchange end, the second throttling end, the second evaporation end and the second gas distribution end of the compression unit in sequence;
the first air circulation loop is communicated to the drying area through an air outlet of the condensing end and then returns to an air inlet of the condensing end from an air return end of the drying area;
the second air circulation loop is communicated to the drying area through an air outlet of the condensing end, then communicated to an air inlet of the evaporating end from an air return end of the drying area, and then communicated to an air inlet of the condensing end from an air outlet of the evaporating end;
and a proportion regulating valve is arranged at the air return end of the drying area and used for regulating the independent operation or the proportion operation of the first air circulation loop and the second air circulation loop.
4. The control method of a heat pump system for dehumidifying and drying according to claim 2 or 3, comprising the steps of:
s1: starting a compression unit, starting a first throttling end and a second throttling end to set opening degrees, and starting and operating a first high-boiling working medium circulation loop and a first low-boiling working medium circulation loop; detecting the relative humidity and the air outlet temperature of the drying area in real time, performing frequency-increasing loading on the compression unit after the operation reaches the set time, and keeping the current working frequency after the compression unit is continuously loaded for the set time T1; the heat prepared by the first condensation end and the second condensation end is sent to the drying area for drying, and most of return air after drying returns to the air inlet end of the condensation end; a small part of the air flows to the first evaporation end and the second evaporation end and then returns to the air inlet end of the condensation end;
establishing first heat exchange of high-low boiling working media based on the second condensation end and the first evaporation end through air circulation returning to the second condensation end through the first evaporation end; establishing second heat exchange of high and low boiling working media through a heat regenerative heat exchange end;
s2: after the air outlet temperature reaches a set high limit value and the moisture content reaches the set high limit value, the compression unit carries out first frequency reduction and load reduction after maintaining the current working frequency for a set time, and keeps the current working frequency after continuously reducing the load for a set time T2; starting and operating a first high-boiling working medium circulation loop, a first low-boiling working medium circulation loop, a second high-boiling working medium circulation loop and a second low-boiling working medium circulation loop; the heat prepared by the first condensation end and the second condensation end is sent to the drying area for drying, and a small part of return air returns to the air inlet end of the condensation end after drying; most of the air flows to the first evaporation end and the second evaporation end and then returns to the air inlet end of the condensation end;
establishing first heat exchange of high-low boiling working media based on the second condensation end and the first evaporation end through air circulation returning to the second condensation end through the first evaporation end; establishing second heat exchange of high-low boiling working media through the self-cascade heat exchange end; establishing third heat exchange of high and low boiling working media through a heat regenerative heat exchange end;
s3: after the air outlet temperature reaches the set low limit value and the moisture content reaches the set low limit value, the compression unit carries out second frequency reduction and load reduction after maintaining the current working frequency for the set time, and keeps the current working frequency after continuously reducing the load for the set time T3; starting and operating a second high-boiling working medium circulation loop and a second low-boiling working medium circulation loop; the heat prepared by the first condensation end is sent to the drying area, and the dried return air returns to the air inlet end of the first condensation end after passing through the second evaporation end;
establishing first heat exchange of high-low boiling working media through the self-cascade heat exchange end; and establishing secondary heat exchange of the high-low boiling working medium through the heat regenerative heat exchange end.
5. The control method of a heat pump system for dehumidifying and drying according to claim 2 or 3, wherein:
the first high-boiling working medium circulation loop is matched with the first low-boiling working medium circulation loop to operate;
the second high-boiling working medium circulation loop is matched with the second low-boiling working medium circulation loop to operate;
the first low-boiling working medium circulation loop and the second low-boiling working medium circulation loop establish proportional adjustment operation through first three-way proportional adjustment arranged among the first gas separation end, the second condensation end and the self-cascade heat exchange end and second three-way proportional adjustment arranged among the second condensation end, the self-cascade heat exchange end and the regenerative heat exchange end;
the first high-boiling working medium circulation loop and the second high-boiling working medium circulation loop establish proportional control operation through third three-way proportional control arranged among the first throttling end, the self-cascade heat exchange end and the first evaporation end and fourth three-way proportional control arranged among the self-cascade heat exchange end, the first evaporation end and the regenerative heat exchange end.
6. The control method of the heat pump system for dehumidifying and drying according to claim 4, wherein:
in step S1, the upscaling is performed according to P1800 +60T1/10,
wherein the content of the first and second substances,
p: motor speed, unit: r/min;
t1: load time, unit: and S.
7. The control method of the heat pump system for dehumidifying and drying according to claim 4, wherein:
in step S2, the first down-conversion and down-loading are performed according to P3900 to 25 × T2/3,
wherein the content of the first and second substances,
p: motor speed, unit: r/min;
t2: off-load time, unit: and S.
8. The control method of the heat pump system for dehumidifying and drying according to claim 4, wherein:
in step S3, the second down-conversion is performed according to P3000-5 × T3,
wherein the content of the first and second substances,
p: motor speed, unit: r/min;
t3: off-load time, unit: and S.
The invention relates to a control method of a heat pump system for dehumidification and drying, aiming at different stages of drying and dehumidification, different responses based on the heat pump system and an air circulation system are established,
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 enhanced vapor injection structure is introduced, so that a low-boiling refrigerant is introduced into a middle 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; 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.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a control step diagram of the present invention;
FIG. 3 is a schematic structural diagram in an embodiment of the present invention;
FIG. 4 is a schematic view of a wind circulation structure according to an embodiment of the present invention;
FIG. 5 is a schematic diagram illustrating the operation of the heat pump system at stage one of the present embodiments;
FIG. 6 is a schematic diagram illustrating the operation of the heat pump system in stage two of the present embodiment;
fig. 7 is a schematic diagram of the operation of the heat pump system in stage three of the embodiment of the present invention.
Detailed Description
Hereinafter, a method for controlling a heat pump system for dehumidifying and drying according to the present invention will be described in further detail with reference to the drawings and embodiments of the present specification.
The control method of the heat pump system for dehumidification and drying as shown in fig. 1 realizes different heat treatment responses by controlling the system, meets the drying requirements of different stages,
the control is established according to two factors of the relative humidity and the outlet air temperature of the drying area and according to different drying stages,
the different stages of drying include: in the early stage of drying, in the middle stage of drying and in the later stage of drying,
the control object points to the following settings in the system: working frequency of the working medium circulation loop, the wind circulation loop and the compression unit;
the working medium is a non-azeotropic mixed working medium, and the working medium circulation loop comprises: the system comprises a first high-boiling working medium circulation loop, a first low-boiling working medium circulation loop, a second high-boiling working medium circulation loop and a second low-boiling working medium circulation loop;
the wind circulation loop comprises: a first wind circulation loop and a second wind circulation loop;
the working frequency of the compression unit is established according to the early drying stage, the middle drying stage and the later drying stage, and the early stage frequency, the middle stage frequency and the later stage frequency are correspondingly formed;
the control method of the heat pump system for dehumidification and drying establishes identification of the drying stage through real-time monitoring of relative humidity and outlet air temperature; by operating the early-stage frequency, operating a first high-boiling working medium circulation loop to be matched with a first low-boiling working medium circulation loop, and combining with wind circulation based on the first wind circulation loop as a main part and a second wind circulation loop as an auxiliary part to respond to the early stage of drying; by operating the middle-term frequency, operating a first high/low boiling working medium circulation loop and a second high/low boiling working medium circulation loop, and combining with the wind circulation taking the first wind circulation loop as the auxiliary based on the second wind circulation loop as the main part to respond to the middle-term drying; and through the operation of later-period frequency, the second high-boiling working medium circulation loop is operated to be matched with the second low-boiling working medium circulation loop, and then the wind circulation based on the second wind circulation loop is combined to respond to the later drying period.
Wherein the content of the first and second substances,
the first high-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the first throttling end, the first evaporation end and the heat regenerative heat exchange end of the compression unit in sequence;
the first low-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the second condensation end, the heat regenerative heat exchange end, the second throttling end, the second evaporation end and the second air distribution end of the compression unit in sequence;
the second high-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the first throttling end, the self-cascade heat exchange end and the regenerative heat exchange end of the compression unit in sequence;
the second low-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the self-cascade heat exchange end, the second throttling end, the second evaporation end and the second air distribution end of the compression unit in sequence;
the first air circulation loop is communicated to the drying area through an air outlet of the condensing end and then returns to an air inlet of the condensing end from an air return end of the drying area;
the second air circulation loop is communicated to the drying area through an air outlet of the condensing end, then communicated to an air inlet of the evaporating end from an air return end of the drying area, and then communicated to an air inlet of the condensing end from an air outlet of the evaporating end;
and a proportion regulating valve is arranged at the air return end of the drying area and used for regulating the independent operation or the proportion operation of the first air circulation loop and the second air circulation loop.
Further, the method can also comprise the following steps:
the first low-boiling working medium circulation loop returns to the gas inlet end of the middle cavity of the compression unit through the gas exhaust end, the first condensation end, the first gas branch end, the second condensation end, the heat regenerative heat exchange end, the second throttling end, the second evaporation end and the second gas branch end of the compression unit in sequence;
and the second low-boiling working medium circulation loop returns to the air inlet end of the middle cavity of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the self-cascade heat exchange end, the second throttling end, the second evaporation end and the second air distribution end of the compression unit in sequence.
As shown in fig. 2, the control method includes the following steps:
s1: starting a compression unit, starting a first throttling end and a second throttling end to set opening degrees, and starting and operating a first high-boiling working medium circulation loop and a first low-boiling working medium circulation loop; detecting the relative humidity and the air outlet temperature of the drying area in real time, performing frequency-increasing loading on the compression unit after the operation reaches the set time, and keeping the current working frequency after the compression unit is continuously loaded for the set time T1; the heat prepared by the first condensation end and the second condensation end is sent to the drying area for drying, and most of return air after drying returns to the air inlet end of the condensation end; a small part of the air flows to the first evaporation end and the second evaporation end and then returns to the air inlet end of the condensation end;
establishing first heat exchange of high-low boiling working media based on the second condensation end and the first evaporation end through air circulation returning to the second condensation end through the first evaporation end; establishing second heat exchange of high and low boiling working media through a heat regenerative heat exchange end;
s2: after the air outlet temperature reaches a set high limit value and the moisture content reaches the set high limit value, the compression unit carries out first frequency reduction and load reduction after maintaining the current working frequency for a set time, and keeps the current working frequency after continuously reducing the load for a set time T2; starting and operating a first high-boiling working medium circulation loop, a first low-boiling working medium circulation loop, a second high-boiling working medium circulation loop and a second low-boiling working medium circulation loop; the heat prepared by the first condensation end and the second condensation end is sent to the drying area for drying, and a small part of return air returns to the air inlet end of the condensation end after drying; most of the air flows to the first evaporation end and the second evaporation end and then returns to the air inlet end of the condensation end;
establishing first heat exchange of high-low boiling working media based on the second condensation end and the first evaporation end through air circulation returning to the second condensation end through the first evaporation end; establishing second heat exchange of high-low boiling working media through the self-cascade heat exchange end; establishing third heat exchange of high and low boiling working media through a heat regenerative heat exchange end;
s3: after the air outlet temperature reaches the set low limit value and the moisture content reaches the set low limit value, the compression unit carries out second frequency reduction and load reduction after maintaining the current working frequency for the set time, and keeps the current working frequency after continuously reducing the load for the set time T3; starting and operating a second high-boiling working medium circulation loop and a second low-boiling working medium circulation loop; the heat prepared by the first condensation end is sent to the drying area, and the dried return air returns to the air inlet end of the first condensation end after passing through the second evaporation end;
establishing first heat exchange of high-low boiling working media through the self-cascade heat exchange end; and establishing secondary heat exchange of the high-low boiling working medium through the heat regenerative heat exchange end.
Wherein the content of the first and second substances,
the first high-boiling working medium circulation loop is matched with the first low-boiling working medium circulation loop to operate;
the second high-boiling working medium circulation loop is matched with the second low-boiling working medium circulation loop to operate;
the first low-boiling working medium circulation loop and the second low-boiling working medium circulation loop establish proportional adjustment operation through first three-way proportional adjustment arranged among the first gas separation end, the second condensation end and the self-cascade heat exchange end and second three-way proportional adjustment arranged among the second condensation end, the self-cascade heat exchange end and the regenerative heat exchange end;
the first high-boiling working medium circulation loop and the second high-boiling working medium circulation loop establish proportional control operation through third three-way proportional control arranged among the first throttling end, the self-cascade heat exchange end and the first evaporation end and fourth three-way proportional control arranged among the self-cascade heat exchange end, the first evaporation end and the regenerative heat exchange end.
Wherein the content of the first and second substances,
in step S1, the upscaling is performed according to P1800 +60T1/10,
wherein the content of the first and second substances,
p: motor speed, unit: r/min;
t1: load time, unit: and S.
Wherein the content of the first and second substances,
in step S2, the first down-conversion and down-loading are performed according to P3900 to 25 × T2/3,
wherein the content of the first and second substances,
p: motor speed, unit: r/min;
t2: off-load time, unit: and S.
Wherein the content of the first and second substances,
in step S3, the second down-conversion is performed according to P3000-5 × T3,
wherein the content of the first and second substances,
p: motor speed, unit: r/min;
t3: off-load time, unit: and S.
Working procedure and examples
The inverter compressor 1 in the present embodiment corresponds to the compression unit described above;
the first condenser 2 in this embodiment corresponds to the first condensation end;
the liquid storage type air separator 3 in the present embodiment corresponds to the first air separation end;
the first electronic expansion valve 4 in this embodiment corresponds to the first throttle end;
the first evaporator 5 in this embodiment corresponds to the first evaporation end;
the heat regenerator 6 in this embodiment corresponds to the heat regenerative heat exchange end;
the second condenser 7 in the present embodiment corresponds to the second condensation end;
the second electronic expansion valve 8 in this embodiment corresponds to the second throttle end;
the second evaporator 9 in this embodiment corresponds to the second evaporation end;
the gas-liquid separator 10 in this embodiment corresponds to the second gas-separation end;
the self-cascade heat exchanger 12 in this embodiment corresponds to the self-cascade heat exchanging end described above;
the three-way electromagnetic valve 11 in this embodiment is used to realize the first three-way proportional adjustment, the second three-way proportional adjustment, the third three-way proportional adjustment, and the fourth three-way proportional adjustment.
Stage one: early stage of dehumidification (relative humidity in system 70-100%)
The system operates: a quasi-self-cascade run, as shown in FIG. 5;
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. 6;
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 ℃, and then passes through the second evaporator 9 and the first evaporator 5 for 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. 7;
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 the throttling action of the first electronic expansion valve 4, completes heat exchange, enters the economizer 6 for further heat exchange to realize overheating, and the refrigerant gas after heat exchange returns 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 structure of the heat pump system is shown in figure 3, and the structure of the wind circulation is shown in figure 4; the corresponding compressor frequency control in the above is as follows:
the method comprises the steps of starting up initially, detecting whether each temperature pressure value in the system is normal or not within 2min, starting an electronic expansion valve to a set initial opening degree after a fan is started for 10S, starting a compressor to an initial frequency, stabilizing for 60S, detecting relative humidity (namely detecting water content) by an air relative humidity sensor in the system, and continuously detecting for 120S when the relative humidity is very low. At this time, every 10S load 60r, the compressor is continuously loaded to 65HZ (3900r/min) from 30HZ (1800r/min), and P is 1800+60T1/10 (where T1 is operating time in S). The rotation speed is stably kept to continuously operate, the temperature and the relative humidity in the air system are continuously detected, so that the moisture content d is calculated, and whether the outlet air temperature reaches 65 ℃ is detected. And when the moisture content reaches a set maximum value d, the temperature reaches a set value and is continuously detected for 20Min, the compressor starts to unload P (3900-25) T2/3 (T is the operation time and unit S) until the temperature is reduced to a target rotating speed of 3000r/Min, the air system starts to act according to a set program after keeping for 15Min, whether the outlet air temperature is reduced to 55 ℃ is detected, and the next program control stage is started after the continuous detection for 10Min, wherein P (3000-5) T3 (T3 is the operation time and unit S) and whether the outlet air temperature reaches 50 ℃ is detected. The relative humidity of air in the air system needs to be reduced to below 5%, the air system is continued for 5min after meeting the two requirements, and a shutdown program (a compressor, a fan and an electronic expansion valve are closed in sequence) is executed.
The invention relates to a control method of a heat pump system for dehumidification and drying, aiming at different stages of drying and dehumidification, different responses based on the heat pump system and an air circulation system are established,
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;
by adopting a non-azeotropic refrigerant and combining a structure of an enhanced vapor injection structure, the low-boiling refrigerant is introduced into the intermediate pressure cavity of the compression unit, so that the effects of supplementing air, reducing the exhaust temperature and reducing the 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.
Claims (8)
1. A control method of a heat pump system for dehumidification and drying realizes different heat treatment responses by controlling the system and meets the drying requirements of different stages, and is characterized in that:
the control is established according to two factors of the relative humidity and the outlet air temperature of the drying area and according to different drying stages,
the different stages of drying include: in the early stage of drying, in the middle stage of drying and in the later stage of drying,
the control object points to the following settings in the system: working frequency of the working medium circulation loop, the wind circulation loop and the compression unit;
the working medium is a non-azeotropic mixed working medium, and the working medium circulation loop comprises: the system comprises a first high-boiling working medium circulation loop, a first low-boiling working medium circulation loop, a second high-boiling working medium circulation loop and a second low-boiling working medium circulation loop;
the wind circulation loop comprises: a first wind circulation loop and a second wind circulation loop;
the working frequency of the compression unit is established according to the early drying stage, the middle drying stage and the later drying stage, and the early stage frequency, the middle stage frequency and the later stage frequency are correspondingly formed;
the control method of the heat pump system for dehumidification and drying establishes identification of the drying stage through real-time monitoring of relative humidity and outlet air temperature; by operating the early-stage frequency, operating a first high-boiling working medium circulation loop to be matched with a first low-boiling working medium circulation loop, and combining with wind circulation based on the first wind circulation loop as a main part and a second wind circulation loop as an auxiliary part to respond to the early stage of drying; by operating the middle-term frequency, operating a first high/low boiling working medium circulation loop and a second high/low boiling working medium circulation loop, and combining with the wind circulation taking the first wind circulation loop as the auxiliary based on the second wind circulation loop as the main part to respond to the middle-term drying; and through the operation of later-period frequency, the second high-boiling working medium circulation loop is operated to be matched with the second low-boiling working medium circulation loop, and then the wind circulation based on the second wind circulation loop is combined to respond to the later drying period.
2. The control method of the heat pump system for dehumidifying and drying according to claim 1, wherein:
the first high-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the first throttling end, the first evaporation end and the heat regenerative heat exchange end of the compression unit in sequence;
the first low-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the second condensation end, the heat regenerative heat exchange end, the second throttling end, the second evaporation end and the second air distribution end of the compression unit in sequence;
the second high-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the first throttling end, the self-cascade heat exchange end and the regenerative heat exchange end of the compression unit in sequence;
the second low-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the self-cascade heat exchange end, the second throttling end, the second evaporation end and the second air distribution end of the compression unit in sequence;
the first air circulation loop is communicated to the drying area through an air outlet of the condensing end and then returns to an air inlet of the condensing end from an air return end of the drying area;
the second air circulation loop is communicated to the drying area through an air outlet of the condensing end, then communicated to an air inlet of the evaporating end from an air return end of the drying area, and then communicated to an air inlet of the condensing end from an air outlet of the evaporating end;
and a proportion regulating valve is arranged at the air return end of the drying area and used for regulating the independent operation or the proportion operation of the first air circulation loop and the second air circulation loop.
3. The control method of the heat pump system for dehumidifying and drying according to claim 1, wherein:
the first high-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the first throttling end, the first evaporation end and the heat regenerative heat exchange end of the compression unit in sequence;
the first low-boiling working medium circulation loop returns to the gas inlet end of the middle cavity of the compression unit through the gas exhaust end, the first condensation end, the first gas branch end, the second condensation end, the heat regenerative heat exchange end, the second throttling end, the second evaporation end and the second gas branch end of the compression unit in sequence;
the second high-boiling working medium circulation loop returns to the air suction end of the compression unit through the exhaust end, the first condensation end, the first air distribution end, the first throttling end, the self-cascade heat exchange end and the regenerative heat exchange end of the compression unit in sequence;
the second low-boiling working medium circulation loop returns to the gas inlet end of the middle cavity of the compression unit through the gas exhaust end, the first condensation end, the first gas distribution end, the self-cascade heat exchange end, the second throttling end, the second evaporation end and the second gas distribution end of the compression unit in sequence;
the first air circulation loop is communicated to the drying area through an air outlet of the condensing end and then returns to an air inlet of the condensing end from an air return end of the drying area;
the second air circulation loop is communicated to the drying area through an air outlet of the condensing end, then communicated to an air inlet of the evaporating end from an air return end of the drying area, and then communicated to an air inlet of the condensing end from an air outlet of the evaporating end;
and a proportion regulating valve is arranged at the air return end of the drying area and used for regulating the independent operation or the proportion operation of the first air circulation loop and the second air circulation loop.
4. The control method of a heat pump system for dehumidifying and drying according to claim 2 or 3, comprising the steps of:
s1: starting a compression unit, starting a first throttling end and a second throttling end to set opening degrees, and starting and operating a first high-boiling working medium circulation loop and a first low-boiling working medium circulation loop; detecting the relative humidity and the air outlet temperature of the drying area in real time, performing frequency-increasing loading on the compression unit after the operation reaches the set time, and keeping the current working frequency after the compression unit is continuously loaded for the set time T1; the heat prepared by the first condensation end and the second condensation end is sent to the drying area for drying, and most of return air after drying returns to the air inlet end of the condensation end; a small part of the air flows to the first evaporation end and the second evaporation end and then returns to the air inlet end of the condensation end;
establishing first heat exchange of high-low boiling working media based on the second condensation end and the first evaporation end through air circulation returning to the second condensation end through the first evaporation end; establishing second heat exchange of high and low boiling working media through a heat regenerative heat exchange end;
s2: after the air outlet temperature reaches a set high limit value and the moisture content reaches the set high limit value, the compression unit carries out first frequency reduction and load reduction after maintaining the current working frequency for a set time, and keeps the current working frequency after continuously reducing the load for a set time T2; starting and operating a first high-boiling working medium circulation loop, a first low-boiling working medium circulation loop, a second high-boiling working medium circulation loop and a second low-boiling working medium circulation loop; the heat prepared by the first condensation end and the second condensation end is sent to the drying area for drying, and a small part of return air returns to the air inlet end of the condensation end after drying; most of the air flows to the first evaporation end and the second evaporation end and then returns to the air inlet end of the condensation end;
establishing first heat exchange of high-low boiling working media based on the second condensation end and the first evaporation end through air circulation returning to the second condensation end through the first evaporation end; establishing second heat exchange of high-low boiling working media through the self-cascade heat exchange end; establishing third heat exchange of high and low boiling working media through a heat regenerative heat exchange end;
s3: after the air outlet temperature reaches the set low limit value and the moisture content reaches the set low limit value, the compression unit carries out second frequency reduction and load reduction after maintaining the current working frequency for the set time, and keeps the current working frequency after continuously reducing the load for the set time T3; starting and operating a second high-boiling working medium circulation loop and a second low-boiling working medium circulation loop; the heat prepared by the first condensation end is sent to the drying area, and the dried return air returns to the air inlet end of the first condensation end after passing through the second evaporation end;
establishing first heat exchange of high-low boiling working media through the self-cascade heat exchange end; and establishing secondary heat exchange of the high-low boiling working medium through the heat regenerative heat exchange end.
5. The control method of a heat pump system for dehumidifying and drying according to claim 2 or 3, wherein:
the first high-boiling working medium circulation loop is matched with the first low-boiling working medium circulation loop to operate;
the second high-boiling working medium circulation loop is matched with the second low-boiling working medium circulation loop to operate;
the first low-boiling working medium circulation loop and the second low-boiling working medium circulation loop establish proportional adjustment operation through first three-way proportional adjustment arranged among the first gas separation end, the second condensation end and the self-cascade heat exchange end and second three-way proportional adjustment arranged among the second condensation end, the self-cascade heat exchange end and the regenerative heat exchange end;
the first high-boiling working medium circulation loop and the second high-boiling working medium circulation loop establish proportional control operation through third three-way proportional control arranged among the first throttling end, the self-cascade heat exchange end and the first evaporation end and fourth three-way proportional control arranged among the self-cascade heat exchange end, the first evaporation end and the regenerative heat exchange end.
6. The control method of the heat pump system for dehumidifying and drying according to claim 4, wherein:
in step S1, the upscaling is performed according to P1800 +60T1/10,
wherein the content of the first and second substances,
p: motor speed unit: r/min;
t1: load time, unit: and S.
7. The control method of the heat pump system for dehumidifying and drying according to claim 4, wherein:
in step S2, the first down-conversion and down-loading are performed according to P3900 to 25 × T2/3,
wherein the content of the first and second substances,
p: motor speed unit: r/min;
t2: off-load time, unit: and S.
8. The control method of the heat pump system for dehumidifying and drying according to claim 4, wherein:
in step S3, the second down-conversion is performed according to P3000-5 × T3,
wherein the content of the first and second substances,
p: motor speed, unit: r/min;
t3: off-load time, unit: and S.
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