CN109442752B - Overlapping type hot air system - Google Patents
Overlapping type hot air system Download PDFInfo
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- CN109442752B CN109442752B CN201811419953.6A CN201811419953A CN109442752B CN 109442752 B CN109442752 B CN 109442752B CN 201811419953 A CN201811419953 A CN 201811419953A CN 109442752 B CN109442752 B CN 109442752B
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- 238000010438 heat treatment Methods 0.000 claims abstract description 100
- 239000003507 refrigerant Substances 0.000 claims abstract description 31
- 238000010257 thawing Methods 0.000 claims abstract description 16
- 239000007788 liquid Substances 0.000 claims description 71
- 230000001502 supplementing effect Effects 0.000 claims description 31
- 230000001105 regulatory effect Effects 0.000 claims description 29
- LVGUZGTVOIAKKC-UHFFFAOYSA-N 1,1,1,2-tetrafluoroethane Chemical compound FCC(F)(F)F LVGUZGTVOIAKKC-UHFFFAOYSA-N 0.000 claims description 6
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 4
- 238000001035 drying Methods 0.000 description 10
- 238000010586 diagram Methods 0.000 description 5
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000003014 reinforcing effect Effects 0.000 description 2
- 238000004781 supercooling Methods 0.000 description 2
- 230000033228 biological regulation Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 239000000110 cooling liquid Substances 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000008018 melting Effects 0.000 description 1
- 238000002844 melting Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H4/00—Fluid heaters characterised by the use of heat pumps
- F24H4/06—Air heaters
-
- 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
-
- 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
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
-
- 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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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The cascade hot air system comprises a closed heating circulation system, wherein a low-temperature hot air outlet, a medium-temperature hot air outlet and three cascade hot air outlets are formed on a hot air pipeline of the cascade hot air system; and a first gradient heating subsystem, a second gradient heating subsystem and a third gradient heating subsystem which respectively supply hot air to the three outlets are formed. Through the arrangement, the cascade hot air system can effectively solve the requirement of stably preparing high-temperature hot water or hot air in winter in northern severe cold areas; the device is provided with different refrigerants, and the high-temperature hot air is prepared by utilizing the characteristics of one of the refrigerants, so that the automatic defrosting function can ensure that the unit operates more stably, and the device can realize higher condensing temperature than the conventional air source heat pump, thereby obtaining higher air outlet temperature.
Description
Technical Field
The utility model belongs to the field of agricultural and sideline product drying, and particularly relates to a cascade hot air system.
Background
Along with the improvement of the requirements of the market on the drying taste and quality of various agricultural and sideline products, manufacturers face the unprecedented challenges on the manufacture of drying equipment. In addition, the country advocates the use of new energy to replace the existing coal-fired and oil-fired boilers so as to realize green and environment-friendly, and the popularization and use of the air source are well-done. However, in the northern winter severe cold weather, the machine is not easy to stably operate, the unit continuously outputs high-temperature hot air, and the evaporation side of the outdoor unit in winter is severely frosted.
The utility model with the application number of 2017210807270 discloses a small and medium-sized grain drying hot air system which comprises a hot air blower, an air supply pipeline, a drying tower blower, a plurality of grain drying towers and air exhaust dust removal equipment; the air heater is an integral machine, wherein a screw compressor, an evaporator, a condenser, a throttle valve, a fresh air filter and the like are arranged in integral equipment, and the screw compressor, the evaporator, the throttle valve and the condenser are connected through pipelines to form a heating loop; the air heater is prefabricated with refrigerant, and the evaporator is provided with an evaporator fan for assisting in improving the heat absorption efficiency of the evaporator; the fresh air filter and the condenser are positioned in a fresh air channel of the air heater, and fresh air is filtered by the fresh air filter and then subjected to heat absorption by the condenser to raise the temperature.
The utility model with the application number of 201720568517X discloses a check type heat pump hot air system taking air as a heat exchange medium, which comprises a high-temperature heat pump system, an air heat energy exchange chamber and a low-temperature heat pump system; the high temperature heat pump system comprises a first condenser, a first compressor, a first evaporator and a first throttle valve; the low temperature heat pump system comprises a second condenser, a second compressor, a second evaporator and a second throttle valve; the first evaporator and the second condenser form an air heat energy exchange chamber. The low-temperature heat pump system and the high-temperature heat pump system are effectively combined, check types of different temperatures are realized, and a third fan is added for use, so that the exchange effect of air heat energy is enhanced.
Disclosure of Invention
In order to effectively solve the requirement of stably preparing high-temperature hot water or hot air in winter in severe cold areas in the north, an overlapping type hot air system is innovated, and the problem that the conventional air source heat pump cannot normally prepare high-temperature hot air in winter when environment is not damaged by using environment-friendly refrigerants is solved. The low-pressure stage system adopts an environment-friendly refrigerant 407C to replace an R22 refrigerant; the high-pressure stage system adopts the environment-friendly refrigerant R134a, the high-temperature hot air is prepared by utilizing the characteristics of the refrigerant, the automatic defrosting function can ensure that the unit operates more stably, and the condensing temperature can be higher than that of a conventional air source heat pump, so that the higher air outlet temperature can be obtained. The technical scheme is as follows:
the utility model provides a cascade hot air system, includes by compressor, cross valve, condenser, reservoir, expansion valve, evaporimeter, cross valve, gas-liquid separator, compressor connect gradually the closed heating circulation system that constitutes, its characterized in that:
three cascade hot air outlets, namely a low-temperature hot air outlet, a medium-temperature hot air outlet and a high-temperature hot air outlet, are formed on a hot air pipeline of the overlapping hot air system;
the cascade hot air system is internally provided with:
the first gradient heating subsystem is used for supplying hot air to the low-temperature hot air outlet;
the second gradient heating subsystem is used for supplying hot air to the middle-temperature hot air outlet;
the third gradient heating subsystem is used for supplying hot air to the high-temperature hot air outlet;
the first gradient heating subsystem is composed of a closed heating loop formed by a first compressor (1-1), a first four-way valve (1-16), a first condenser (1-3-2), a first liquid storage device (1-4), a first expansion valve (1-6), a first evaporator (1-7), a first four-way valve (1-16), a first gas-liquid separator (1-8) and a first compressor (1-1) which are connected in sequence;
the third gradient heating subsystem is composed of a closed heating loop formed by a second compressor (2-1), a second four-way valve (2-2), a second condenser (2-3), a second liquid storage device (2-4), a second expansion valve (2-7), a second evaporator (1-3-1), a second four-way valve (2-2), a second gas-liquid separator (2-8) and a second compressor (2-1) which are connected in sequence;
the second gradient heating subsystem is composed of a first condenser in the first gradient heating subsystem, a second evaporator in the third gradient heating subsystem and different flow channels built in the same heat exchanger.
The cascade hot air system is characterized in that:
the refrigerant for circulation in the first gradient heating subsystem and the refrigerant for circulation in the third gradient heating subsystem are different.
The cascade hot air system is characterized in that:
a first economizer (1-5) is arranged between the first liquid storage device (1-4) and the first expansion valve (1-6);
the liquid inlet of the first economizer (1-5) is connected with the outlet of the first liquid reservoir (1-4);
the liquid outlet of the first economizer (1-5) is connected with the inlet of the first expansion valve (1-6);
the air supplementing port of the first economizer (1-5) is connected with the inlet of the first compressor;
a first air supplementing capillary tube (1-12) is arranged between a liquid outlet of the first economizer (1-5) and a self-circulation air outlet, and a first electromagnetic valve (1-13) is arranged on the first air supplementing capillary tube (1-12).
The cascade hot air system is characterized in that:
a second economizer (2-5) is arranged between the second liquid storage device (2-4) and the second expansion valve (2-7);
the liquid inlet of the second economizer (2-5) is connected with the outlet of the second liquid reservoir (2-4);
the liquid outlet of the second economizer (2-5) is connected with the inlet of the second expansion valve (2-7);
the air supplementing port of the second economizer (2-5) is connected with the inlet of the second compressor;
a second air supplementing capillary tube (2-9) is arranged between a liquid outlet of the second economizer (2-5) and the self-circulation air outlet, and a second electromagnetic valve (2-6) is arranged on the second air supplementing capillary tube (2-9).
The cascade hot air system is characterized in that:
a first three-way proportional regulating valve (1-14) is arranged on a pipeline of the first four-way valve (1-16) leading to the first condenser (1-3-2),
the inlet of the first three-way proportional regulating valve (1-14) is connected with the first four-way valve (1-16) through a pipeline;
the first outlet of the first three-way proportional regulating valve (1-14) is connected with the first condenser (1-3-2) through a pipeline;
the second outlet of the first three-way proportional regulating valve (1-14) is connected with the second evaporator (1-3-1) through a pipeline;
a second three-way proportional regulating valve (1-15) is arranged on a connecting pipeline of the first condenser (1-3-2) and the first liquid storage device (1-4);
the first inlet of the second three-way proportional regulating valve (1-15) is connected with the first condenser (1-3-2) through a pipeline;
the second inlet of the second three-way proportional regulating valve (1-15) is connected with the second evaporator (1-3-1) through a pipeline;
the outlet of the second three-way proportional control valve (1-15) is connected with the first liquid reservoir (1-14) through a pipeline.
The cascade hot air system is characterized in that:
the first compressor and the second compressor are variable frequency compressors.
The cascade hot air system is characterized in that:
a third electromagnetic valve (1-9) and a defrosting valve (1-10) which are connected through a pipeline are further arranged on the side of a first expansion valve (1-6) in the first gradient heating subsystem;
the third electromagnetic valve (1-9) connected with the pipeline is connected with the pipeline where the defrosting valve (1-10) is located and the pipeline where the first expansion valve (1-6) is located in parallel, and the first liquid storage device (1-4) and the first evaporator (1-7) are connected in parallel.
The utility model relates to a cascade hot air system,
firstly, two sets of closed hot air circulation structures which are sequentially connected by a compressor, a four-way valve, a condenser, a liquid reservoir, an expansion valve, an evaporator, a four-way valve, a gas-liquid separator and the compressor are arranged; the environment-friendly refrigerant 407C and the environment-friendly refrigerant R134a are respectively filled in the two sets of closed hot air circulation structures; the system comprises a first gradient heating subsystem and a third gradient heating subsystem, wherein the first gradient heating subsystem and the third gradient heating subsystem are used for respectively forming low-temperature hot air making and high-temperature hot air making;
secondly, arranging a condenser in the first gradient heating subsystem and an evaporator in the third gradient heating subsystem in a shell to form a second gradient heating subsystem;
accordingly, through the two sets of closed hot air circulation structures, and through establishing an association relationship between the two sets of closed hot air circulation structures, the cascade hot air supply formed by the first gradient heating subsystem, the second gradient heating subsystem and the third gradient heating subsystem of the cascade hot air system is formed.
And thirdly, respectively arranging an economizer and a corresponding air supplementing capillary tube in the first gradient heating subsystem and the third gradient heating subsystem, and establishing level adjustment in the respective systems so as to form multi-level environment adaptability adjustment.
Then, the compressors in the two closed hot air circulation structures are all set to be variable frequency compressors for reinforcing multi-level environment adaptability adjustment, so that more sufficient multi-level adaptation is formed.
Finally, aiming at the second gradient heating subsystem, establishing hierarchical heating air adjustment based on the second gradient heating subsystem through two three-way proportional adjustment valves, and forming integral hierarchical adjustment in the system in concert with the established hierarchical adjustment to fully respond to different environments;
on the basis of the above, a defrosting valve and a corresponding electromagnetic valve which are arranged in parallel with the first expansion valve are also arranged in the first gradient heating subsystem so as to form an automatic defrosting structure based on the first gradient heating subsystem.
In summary, through the arrangement, the cascade hot air system can effectively solve the requirement of stably preparing high-temperature hot water or hot air in winter in northern severe cold areas; the environment-friendly refrigerant is not destroyed, and meanwhile, the problem that the conventional air source heat pump cannot normally prepare high-temperature hot air in winter is effectively solved, which comprises the following steps: for the first gradient heating subsystem, an environment-friendly refrigerant R407C is adopted to replace an R22 refrigerant; aiming at the third gradient heating subsystem, the environment-friendly refrigerant R134a is adopted, the high-temperature hot air is prepared by utilizing the characteristics of the refrigerant, the automatic defrosting function can ensure that the unit operates more stably, and the condensing temperature can be higher than that of a conventional air source heat pump, so that the higher air outlet temperature can be obtained.
Drawings
FIG. 1 is a schematic block diagram of the structure of the present utility model;
FIG. 2 is a schematic diagram of the structure of the present utility model;
FIG. 3 is a schematic diagram of a low temperature air supply operation flow of the present utility model;
FIG. 4 is a schematic diagram of a medium temperature air supply operation flow of the present utility model;
FIG. 5 is a schematic flow chart of the air supply circuit in the middle temperature air supply operation of the utility model;
FIG. 6 is a schematic diagram illustrating the operation of high temperature air supply in the present utility model;
fig. 7 is a schematic view of automatic defrosting in the present utility model.
In the drawing the view of the figure,
1-1 is a first compressor;
1-16 are first four-way valves;
1-3-2 is a first condenser;
1-4 is a first reservoir;
1-6 are first expansion valves;
1-7 are first evaporators;
1-16 are the first four-way valve of the present utility model;
1-8 are first gas-liquid separators;
1-9 are third electromagnetic valves;
1-10 are defrost valves;
1-12 are first air supplementing capillaries;
1-13 are first solenoid valves;
1-14 are first three-way proportional control valves;
1-15 is a second three-way proportional control valve;
2-1 is a second compressor;
2-2 is a second four-way valve;
2-3 is a second condenser;
2-4 is a second reservoir;
2-7 is a second expansion valve;
1-3-1 is a second evaporator;
2-2 is a second four-way valve;
2-8 is a second gas-liquid separator;
2-5 is a second economizer;
2-6 is a second electromagnetic valve;
and 2-9 is a second air supplementing capillary tube.
Detailed Description
A cascade hot air system according to the utility model will be described in further detail below with reference to the drawings and the detailed description.
The cascade hot air system shown in fig. 1 comprises a closed heating circulation system formed by sequentially connecting a compressor, a four-way valve, a condenser, a liquid reservoir, an expansion valve, an evaporator, a four-way valve, a gas-liquid separator and a compressor, wherein a hot air pipeline of the cascade hot air system is provided with three cascade hot air outlets, namely a low-temperature hot air outlet, a medium-temperature hot air outlet and a high-temperature hot air outlet;
the cascade hot air system is internally provided with:
the first gradient heating subsystem is used for supplying hot air to the low-temperature hot air outlet;
the second gradient heating subsystem is used for supplying hot air to the middle-temperature hot air outlet;
and the third gradient heating subsystem is used for supplying hot air to the high-temperature hot air outlet.
Wherein,
as shown in fig. 2, the first gradient heating subsystem is composed of a closed heating loop composed of a first compressor (1-1), a first four-way valve (1-16), a first condenser (1-3-2), a first liquid storage (1-4), a first expansion valve (1-6), a first evaporator (1-7), a first four-way valve (1-16), a first gas-liquid separator (1-8) and a first compressor (1-1) which are connected in sequence;
the third gradient heating subsystem is composed of a closed heating loop formed by a second compressor (2-1), a second four-way valve (2-2), a second condenser (2-3), a second liquid storage device (2-4), a second expansion valve (2-7), a second evaporator (1-3-1), a second four-way valve (2-2), a second gas-liquid separator (2-8) and a second compressor (2-1) which are connected in sequence;
the second gradient heating subsystem is composed of a first condenser in the first gradient heating subsystem, a second evaporator in the third gradient heating subsystem and different flow channels built in the same heat exchanger.
Wherein,
the refrigerant for circulation in the first gradient heating subsystem and the refrigerant for circulation in the third gradient heating subsystem are two different types, and specifically: the refrigerant for circulation in the first gradient subsystem is R407C; the circulating refrigerant in the first gradient subsystem is R134a.
Wherein,
a first economizer (1-5) is arranged between the first liquid storage device (1-4) and the first expansion valve (1-6);
the liquid inlet of the first economizer (1-5) is connected with the outlet of the first liquid reservoir (1-4);
the liquid outlet of the first economizer (1-5) is connected with the inlet of the first expansion valve (1-6);
the air supplementing port of the first economizer (1-5) is connected with the inlet of the first compressor;
a first air supplementing capillary tube (1-12) is arranged between a liquid outlet of the first economizer (1-5) and a self-circulation air outlet, and a first electromagnetic valve (1-13) is arranged on the first air supplementing capillary tube (1-12).
Wherein,
a second economizer (2-5) is arranged between the second liquid storage device (2-4) and the second expansion valve (2-7);
the liquid inlet of the second economizer (2-5) is connected with the outlet of the second liquid reservoir (2-4);
the liquid outlet of the second economizer (2-5) is connected with the inlet of the second expansion valve (2-7);
the air supplementing port of the second economizer (2-5) is connected with the inlet of the second compressor;
a second air supplementing capillary tube (2-9) is arranged between a liquid outlet of the second economizer (2-5) and the self-circulation air outlet, and a second electromagnetic valve (2-6) is arranged on the second air supplementing capillary tube (2-9).
Wherein,
a first three-way proportional regulating valve (1-14) is arranged on a pipeline of the first four-way valve (1-16) leading to the first condenser (1-3-2),
the inlet of the first three-way proportional regulating valve (1-14) is connected with the first four-way valve (1-16) through a pipeline;
the first outlet of the first three-way proportional regulating valve (1-14) is connected with the first condenser (1-3-2) through a pipeline;
the second outlet of the first three-way proportional regulating valve (1-14) is connected with the second evaporator (1-3-1) through a pipeline;
a second three-way proportional regulating valve (1-15) is arranged on a connecting pipeline of the first condenser (1-3-2) and the first liquid storage device (1-4);
the first inlet of the second three-way proportional regulating valve (1-15) is connected with the first condenser (1-3-2) through a pipeline;
the second inlet of the second three-way proportional regulating valve (1-15) is connected with the second evaporator (1-3-1) through a pipeline;
the outlet of the second three-way proportional control valve (1-15) is connected with the first liquid reservoir (1-14) through a pipeline.
Wherein,
the first compressor and the second compressor are variable frequency compressors.
Wherein,
a third electromagnetic valve (1-9) and a defrosting valve (1-10) which are connected through a pipeline are further arranged on the side of a first expansion valve (1-6) in the first gradient heating subsystem;
the third electromagnetic valve (1-9) connected with the pipeline is connected with the pipeline where the defrosting valve (1-10) is located and the pipeline where the first expansion valve (1-6) is located in parallel, and the first liquid storage device (1-4) and the first evaporator (1-7) are connected in parallel.
Working principles and examples
The dynamic operation mode of the system is described:
according to the difference of the required temperatures of the specific drying functional areas, the related components in the system are regulated to achieve the aim of different air supply temperatures. The specific actions are as follows:
1. low temperature air supply operation
The operation mode is more suitable for places with low early drying temperature, only the first gradient heating subsystem is used at the moment, condensation heat is directly discharged to heat utilization places, the operation cost of the mode is relatively low, and the frequency of the compressor is increased when the load is increased so as to meet the heat utilization requirement. When the external environment temperature is reduced, the load is met through the frequency conversion system, the temperature is continuously reduced, and the air supplementing electromagnetic valve is opened to offset the energy loss caused by the reduction of the ring temperature. When the temperature is above 0 ℃, adopting variable frequency regulation; adopting the air supplementing enthalpy increasing adjustment based on an economizer when the temperature is between 0 ℃ and-12 ℃; when the temperature is lower than-12 ℃, the combination of variable frequency adjustment based on a variable frequency compressor and air supplementing enthalpy increasing adjustment based on an economizer is adopted for adjustment.
The flow is shown in fig. 3.
2. Medium temperature air supply operation
For the middle drying stage, the temperature required by the drying place is relatively increased, and the temperature of the condensed air outlet of the first gradient and the third gradient is mixed to finally reach the design temperature requirement.
The flow is shown in fig. 4.
When the ambient temperature is reduced to minus, the low-temperature-level system starts the air supplementing loop, and part of the refrigerant liquid passes through the economizers 1-5, so that the supercooling degree of the refrigerant liquid in the system is increased, and the heating capacity is improved.
The flow is shown in fig. 5.
The three-way valves 1-14 and 1-15 in the first gradient heating subsystem are adjusted to adjust the flow distributed in the two-way valve 1-3-1 and 1-3-2, and the low-temperature hot air produced by the two-way valve 1-3-2 is mixed with the high-temperature hot air produced by the two-way valve 2-3 to be changed into medium-temperature hot air which is then sent to a heat utilization place.
3. High temperature air supply operation as shown in fig. 6;
when a higher air outlet temperature is required to be prepared, a loop of the first gradient heating subsystem is started, and then a loop of the third gradient heating subsystem is started, and condensation heat in the first gradient heating subsystem is transferred to the third gradient heating subsystem through the evaporative condenser 1-3-2, so that the reliability and stability of the third gradient heating subsystem in operation at a low environment temperature are greatly improved. When the severe weather is met, a gas supplementing loop in the first gradient heating subsystem is started, and the enthalpy value of the cooling liquid in the system is increased, so that the effect of increasing the heating capacity is achieved; and simultaneously, the frequency of the second compressor is increased, and the circulating flow of the refrigerant of the system is directly increased through the increasing frequency, so that the heat generation quantity is increased. In addition, the compressor can safely run and stably output under the working condition of a great compression ratio. When the air outlet temperature of the third gradient heating subsystem is very high, an air supplementing loop in the third gradient heating subsystem is started, the supercooling function of condensed refrigerant liquid is realized, the heating capacity of the system is increased, meanwhile, the excessive increase of the exhaust temperature is well restrained, and the stability of the system under high-temperature operation is ensured.
4. Automatic defrost as shown in fig. 7;
when the machine detection system reaches the defrosting condition, the first condensing side fan stops running. And switching the first four-way valve to bypass the hot gas to the first evaporator, and melting hot frost in the fins by utilizing sensible heat and latent heat of the superheated refrigerant gas.
The utility model relates to a cascade hot air system,
firstly, two sets of closed hot air circulation structures which are sequentially connected by a compressor, a four-way valve, a condenser, a liquid reservoir, an expansion valve, an evaporator, a four-way valve, a gas-liquid separator and the compressor are arranged; the environment-friendly refrigerant 407C and the environment-friendly refrigerant R134a are respectively filled in the two sets of closed hot air circulation structures; the system comprises a first gradient heating subsystem and a third gradient heating subsystem, wherein the first gradient heating subsystem and the third gradient heating subsystem are used for respectively forming low-temperature hot air making and high-temperature hot air making;
secondly, arranging a condenser in the first gradient heating subsystem and an evaporator in the third gradient heating subsystem in a shell to form a second gradient heating subsystem;
accordingly, through the two sets of closed hot air circulation structures, and through establishing an association relationship between the two sets of closed hot air circulation structures, the cascade hot air supply formed by the first gradient heating subsystem, the second gradient heating subsystem and the third gradient heating subsystem of the cascade hot air system is formed.
And thirdly, respectively arranging an economizer and a corresponding air supplementing capillary tube in the first gradient heating subsystem and the third gradient heating subsystem, and establishing level adjustment in the respective systems so as to form multi-level environment adaptability adjustment.
Then, the compressors in the two closed hot air circulation structures are all set to be variable frequency compressors for reinforcing multi-level environment adaptability adjustment, so that more sufficient multi-level adaptation is formed.
Finally, aiming at the second gradient heating subsystem, establishing hierarchical heating air adjustment based on the second gradient heating subsystem through two three-way proportional adjustment valves, and forming integral hierarchical adjustment in the system in concert with the established hierarchical adjustment to fully respond to different environments;
on the basis of the above, a defrosting valve and a corresponding electromagnetic valve which are arranged in parallel with the first expansion valve are also arranged in the first gradient heating subsystem so as to form an automatic defrosting structure based on the first gradient heating subsystem.
In summary, through the arrangement, the cascade hot air system can effectively solve the requirement of stably preparing high-temperature hot water or hot air in winter in northern severe cold areas; the environment-friendly refrigerant is not destroyed, and meanwhile, the problem that the conventional air source heat pump cannot normally prepare high-temperature hot air in winter is effectively solved, which comprises the following steps: for the first gradient heating subsystem, an environment-friendly refrigerant R407C is adopted to replace an R22 refrigerant; aiming at the third gradient heating subsystem, the environment-friendly refrigerant R134a is adopted, the high-temperature hot air is prepared by utilizing the characteristics of the refrigerant, the automatic defrosting function can ensure that the unit operates more stably, and the condensing temperature can be higher than that of a conventional air source heat pump, so that the higher air outlet temperature can be obtained.
Claims (7)
1. The utility model provides a cascade hot air system, includes by compressor, cross valve, condenser, reservoir, expansion valve, evaporimeter, cross valve, gas-liquid separator, compressor connect gradually the closed heating circulation system that constitutes, its characterized in that:
three cascade hot air outlets, namely a low-temperature hot air outlet, a medium-temperature hot air outlet and a high-temperature hot air outlet, are formed on a hot air pipeline of the overlapping hot air system;
the cascade hot air system is internally provided with:
the first gradient heating subsystem is used for supplying hot air to the low-temperature hot air outlet;
the second gradient heating subsystem is used for supplying hot air to the middle-temperature hot air outlet;
the third gradient heating subsystem is used for supplying hot air to the high-temperature hot air outlet;
the first gradient heating subsystem is composed of a closed heating loop formed by a first compressor (1-1), a first four-way valve (1-16), a first condenser (1-3-2), a first liquid storage device (1-4), a first expansion valve (1-6), a first evaporator (1-7), a first four-way valve (1-16), a first gas-liquid separator (1-8) and a first compressor (1-1) which are connected in sequence;
the third gradient heating subsystem is composed of a closed heating loop formed by a second compressor (2-1), a second four-way valve (2-2), a second condenser (2-3), a second liquid storage device (2-4), a second expansion valve (2-7), a second evaporator (1-3-1), a second four-way valve (2-2), a second gas-liquid separator (2-8) and a second compressor (2-1) which are connected in sequence;
the second gradient heating subsystem is composed of a first condenser in the first gradient heating subsystem, a second evaporator in the third gradient heating subsystem and different flow channels built in the same heat exchanger;
the refrigerant for circulation in the first gradient heating subsystem and the refrigerant for circulation in the third gradient heating subsystem are different;
the first gradient heating subsystem adopts an environment-friendly refrigerant R407C; the third gradient heating subsystem adopts an environment-friendly refrigerant R134a.
2. The cascade hot air system of claim 1, wherein:
a first economizer (1-5) is arranged between the first liquid storage device (1-4) and the first expansion valve (1-6);
the liquid inlet of the first economizer (1-5) is connected with the outlet of the first liquid reservoir (1-4);
the liquid outlet of the first economizer (1-5) is connected with the inlet of the first expansion valve (1-6);
the air supplementing port of the first economizer (1-5) is connected with the inlet of the first compressor;
a first air supplementing capillary tube (1-12) is arranged between a liquid outlet of the first economizer (1-5) and a self-circulation air outlet, and a first electromagnetic valve (1-13) is arranged on the first air supplementing capillary tube (1-12).
3. The cascade hot air system of claim 1, wherein:
a second economizer (2-5) is arranged between the second liquid storage device (2-4) and the second expansion valve (2-7);
the liquid inlet of the second economizer (2-5) is connected with the outlet of the second liquid reservoir (2-4);
the liquid outlet of the second economizer (2-5) is connected with the inlet of the second expansion valve (2-7);
the air supplementing port of the second economizer (2-5) is connected with the inlet of the second compressor;
a second air supplementing capillary tube (2-9) is arranged between a liquid outlet of the second economizer (2-5) and the self-circulation air outlet, and a second electromagnetic valve (2-6) is arranged on the second air supplementing capillary tube (2-9).
4. The cascade hot air system of claim 1, wherein:
a first three-way proportional regulating valve (1-14) is arranged on a pipeline of the first four-way valve (1-16) leading to the first condenser (1-3-2),
the inlet of the first three-way proportional regulating valve (1-14) is connected with the first four-way valve (1-16) through a pipeline;
the first outlet of the first three-way proportional regulating valve (1-14) is connected with the first condenser (1-3-2) through a pipeline;
the second outlet of the first three-way proportional regulating valve (1-14) is connected with the second evaporator (1-3-1) through a pipeline;
a second three-way proportional regulating valve (1-15) is arranged on a connecting pipeline of the first condenser (1-3-2) and the first liquid storage device (1-4);
the first inlet of the second three-way proportional regulating valve (1-15) is connected with the first condenser (1-3-2) through a pipeline;
the second inlet of the second three-way proportional regulating valve (1-15) is connected with the second evaporator (1-3-1) through a pipeline;
the outlet of the second three-way proportional control valve (1-15) is connected with the first liquid reservoir (1-4) through a pipeline.
5. The cascade hot air system of claim 2, wherein:
a second economizer (2-5) is arranged between the second liquid storage device (2-4) and the second expansion valve (2-7);
the liquid inlet of the second economizer (2-5) is connected with the outlet of the second liquid reservoir (2-4);
the liquid outlet of the second economizer (2-5) is connected with the inlet of the second expansion valve (2-7);
the air supplementing port of the second economizer (2-5) is connected with the inlet of the second compressor;
a second air supplementing capillary tube (2-9) is arranged between a liquid outlet of the second economizer (2-5) and a self-circulation air outlet, and a second electromagnetic valve (2-6) is arranged on the second air supplementing capillary tube (2-9);
a first three-way proportional regulating valve (1-14) is arranged on a pipeline of the first four-way valve (1-16) leading to the first condenser (1-3-2),
the inlet of the first three-way proportional regulating valve (1-14) is connected with the first four-way valve (1-16) through a pipeline;
the first outlet of the first three-way proportional regulating valve (1-14) is connected with the first condenser (1-3-2) through a pipeline;
the second outlet of the first three-way proportional regulating valve (1-14) is connected with the second evaporator (1-3-1) through a pipeline;
a second three-way proportional regulating valve (1-15) is arranged on a connecting pipeline of the first condenser (1-3-2) and the first liquid storage device (1-4);
the first inlet of the second three-way proportional regulating valve (1-15) is connected with the first condenser (1-3-2) through a pipeline;
the second inlet of the second three-way proportional regulating valve (1-15) is connected with the second evaporator (1-3-1) through a pipeline;
the outlet of the second three-way proportional control valve (1-15) is connected with the first liquid reservoir (1-4) through a pipeline.
6. The cascade hot air system of claim 1, wherein:
the first compressor and the second compressor are variable frequency compressors.
7. The cascade hot air system of claim 1, wherein:
a third electromagnetic valve (1-9) and a defrosting valve (1-10) which are connected through a pipeline are further arranged on the side of a first expansion valve (1-6) in the first gradient heating subsystem;
the third electromagnetic valve (1-9) connected with the pipeline is connected with the pipeline where the defrosting valve (1-10) is located and the pipeline where the first expansion valve (1-6) is located in parallel, and the first liquid storage device (1-4) and the first evaporator (1-7) are connected in parallel.
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| CN110701664B (en) * | 2019-11-11 | 2023-05-05 | 江苏天舒电器有限公司 | Wide-ring-temperature multistage water outlet variable-frequency air energy cascade heat engine system and working method thereof |
| CN111595002B (en) * | 2020-05-18 | 2021-09-17 | 广东美的暖通设备有限公司 | Air conditioning system, control method thereof, control device thereof and readable storage medium |
| CN113959096A (en) * | 2021-11-05 | 2022-01-21 | 广州黑马科技有限公司 | Heat pump device capable of generating high-temperature air |
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