CN114034183A - Totally-enclosed high-precision temperature and humidity independent control heat pump drying system - Google Patents
Totally-enclosed high-precision temperature and humidity independent control heat pump drying system Download PDFInfo
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- CN114034183A CN114034183A CN202111551313.2A CN202111551313A CN114034183A CN 114034183 A CN114034183 A CN 114034183A CN 202111551313 A CN202111551313 A CN 202111551313A CN 114034183 A CN114034183 A CN 114034183A
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- way valve
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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
- F26B21/001—Drying-air generating units, e.g. movable, independent of drying enclosure
- F26B21/002—Drying-air generating units, e.g. movable, independent of drying enclosure heating the drying air indirectly, i.e. using a heat exchanger
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- A—HUMAN NECESSITIES
- A24—TOBACCO; CIGARS; CIGARETTES; SIMULATED SMOKING DEVICES; SMOKERS' REQUISITES
- A24B—MANUFACTURE OR PREPARATION OF TOBACCO FOR SMOKING OR CHEWING; TOBACCO; SNUFF
- A24B3/00—Preparing tobacco in the factory
- A24B3/04—Humidifying or drying tobacco bunches or cut tobacco
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- A—HUMAN NECESSITIES
- A24—TOBACCO; CIGARS; CIGARETTES; SIMULATED SMOKING DEVICES; SMOKERS' REQUISITES
- A24B—MANUFACTURE OR PREPARATION OF TOBACCO FOR SMOKING OR CHEWING; TOBACCO; SNUFF
- A24B3/00—Preparing tobacco in the factory
- A24B3/10—Roasting or cooling tobacco
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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
- F26B21/004—Nozzle assemblies; Air knives; Air distributors; Blow boxes
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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
- F26B21/086—Humidity by condensing the moisture in the drying medium, which may be recycled, e.g. using a heat pump cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F26—DRYING
- F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
- F26B21/00—Arrangements or duct systems, e.g. in combination with pallet boxes, for supplying and controlling air or gases for drying solid materials or objects
- F26B21/06—Controlling, e.g. regulating, parameters of gas supply
- F26B21/10—Temperature; Pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F26—DRYING
- F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
- F26B25/00—Details of general application not covered by group F26B21/00 or F26B23/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F26—DRYING
- F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
- F26B2200/00—Drying processes and machines for solid materials characterised by the specific requirements of the drying good
- F26B2200/22—Tobacco leaves
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The technology discloses a totally-enclosed high-precision temperature and humidity independent control heat pump drying system, taking the flow direction of air flow as reference, a first indoor heat exchanger is connected between an air inlet precooling channel and an air outlet baffling channel of a plate-fin heat exchanger, a refrigerant output pipe of a compressor is connected with a first input port of a first four-way valve, one pipeline of a second indoor heat exchanger is connected with the first four-way valve, the other pipeline of the second indoor heat exchanger leads out two paths, the first pipeline is connected with a first electromagnetic switch valve, the second pipeline is sequentially connected with a first one-way valve and a second four-way valve, the second four-way valve is connected with the first indoor heat exchanger, a second electromagnetic switch valve is arranged on a third pipeline led out from a second pipe orifice of the first indoor heat exchanger, the first electromagnetic switch valve and the second electromagnetic switch valve are mutually communicated and then connected with an outdoor heat exchanger, and the first four-way valve, the second four-way valve, the first electromagnetic switch valve and the second electromagnetic switch valve are mutually replaced, the removal and the replacement of different modes of the drying system are realized, and the function integration is strong.
Description
Technical Field
The invention relates to a totally-enclosed high-precision temperature and humidity independent control heat pump drying system.
Background
The traditional heat pump dryer utilizes a heat pump system as a heat source to continuously heat a drying room, and the humidity of the tobacco curing room is reduced by introducing fresh air to dry tobacco. Such drying systems have the following disadvantages: firstly, low-temperature fresh air needs to be introduced during moisture removal, so that the heat dissipation loss is very serious; secondly, when the environmental temperature is low, the heat absorption capacity of the heat pump from the environment is reduced, the energy efficiency in the tobacco curing process is greatly reduced, even the situation of insufficient heat occurs, and the constant-temperature baking effect is difficult to achieve; thirdly, the effective components of the materials are taken away by introducing excessive fresh air, so that the effective components are greatly reduced after the materials are dried, and the drying quality of the materials is reduced; fourthly, in non-material drying seasons, the drying and baking room is dull and serious and occupies a large area, which brings great waste to resources.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a totally-enclosed high-precision temperature and humidity independent control heat pump drying system.
The invention aims to be realized by the following technical scheme: a totally-enclosed high-precision temperature and humidity independent control heat pump drying system comprises an outdoor component group and an indoor component group, wherein the outdoor component group comprises a compressor, an outdoor heat exchanger, a liquid storage device, a throttle valve and a gas-liquid separator, the indoor component group comprises a first indoor heat exchanger, a second indoor heat exchanger and a plate-fin heat exchanger, the flowing direction of air flow is taken as reference, the first indoor heat exchanger is positioned in an upwind area of the air flow, the second indoor heat exchanger is positioned in a downwind area, the first indoor heat exchanger is connected between an air inlet precooling channel and an air outlet baffling channel of the plate-fin heat exchanger, the gas-liquid separator is arranged on a refrigerant input pipe of the compressor, a refrigerant output pipe of the compressor is connected with a first input port of a first four-way valve, a pipeline of the second indoor heat exchanger is connected with a first right output port of the first four-way valve, and two pipelines are led out from the other pipeline of the second indoor heat exchanger, the first pipeline is connected with a first electromagnetic switch valve, the second pipeline is sequentially connected with a first one-way valve and a second four-way valve, a second right-side output port of the second four-way valve is connected with a first pipe orifice of the first indoor heat exchanger, a second electromagnetic switch valve is arranged on a third pipeline led out from a second pipe orifice of the first indoor heat exchanger, the first electromagnetic switch valve and the second electromagnetic switch valve are connected with a first connecting port of the outdoor heat exchanger after being mutually communicated, a second connecting port of the outdoor heat exchanger is connected with a second left-side output port of the second four-way valve, a first left-side output port of the first four-way valve is firstly connected with the second one-way valve and then connected with the second pipeline between the first one-way valve and the second four-way valve, and a first middle output port of the first four-way valve and a second middle output port of the second four-way valve are mutually communicated and connected with an inlet of the gas-liquid separator.
And a bridge type loop is arranged between the junction of the first electromagnetic switch valve and the second electromagnetic switch valve and the first connection port of the outdoor heat exchanger.
A liquid reservoir and a throttle valve are sequentially connected to the loop bypass of the bridge loop along the flowing direction of the refrigerant.
The first indoor heat exchanger, the second indoor heat exchanger and the outdoor heat exchanger are coil type heat exchangers.
The bridge circuit is composed of four one-way valves, pipes led from the first electromagnetic switch valve and the second electromagnetic switch valve are divided into two paths, each path is provided with a pair of one-way valves, the pair of one-way valves of the first path face to be opposite, and the pair of one-way valves of the second path face back to back.
The bridge-type loop is composed of four one-way valves, pipes led from the first electromagnetic switch valve and the second electromagnetic switch valve are divided into two paths, each path is provided with a pair of one-way valves, the pair of one-way valves of the first path face to face oppositely, the pair of one-way valves of the second path face back to back, one end of the loop-back bypass is connected with a pipeline between the two one-way valves of the first path, and the other end of the loop-back bypass is connected with a pipeline between the two one-way valves of the second path.
After adopting this technical scheme, compare with prior art, this technical scheme has following advantage: this technique heat pump drying system can realize multiple stoving mode, including rapid heating up stoving mode, constant temperature dehumidification mode, cooling dehumidification mode and cold-stored mode, above-mentioned mode is at the stoving process according to the operation of different hot humid load collocation, make whole stoving process can realize totally closed stoving, do not have the new trend exchange with the external world, can keep the active ingredient by the baked material, and can regard as the use of the cold-stored article of low temperature walk-in, the wide application is in the tobacco stoving room of taking cold storage function, other fields that have totally closed stoving demand such as the stoving cellular fluid recovery of high added value agricultural product.
Drawings
FIG. 1 is a block diagram of mode one heating ramp mode of the present invention;
FIG. 2 is a structural diagram of the overheating trimming excess heat in the mode two constant temperature dehumidification mode of the present invention;
FIG. 3 is a structural diagram of supercooling temperature rise in the constant temperature dehumidification mode II of the present invention;
FIG. 4 is a block diagram of a cooling and dehumidifying mode III of the present invention;
FIG. 5 is a block diagram of the four maximum cooling modes of the present invention; .
Detailed Description
Embodiments of the present invention will be described below with reference to the accompanying drawings and related embodiments, wherein the following related embodiments are merely preferred embodiments for better illustrating the present invention itself, and the embodiments of the present invention are not limited to the following embodiments, and the present invention relates to the related essential parts in the technical field, which should be regarded as the known technology in the technical field and can be known and grasped by those skilled in the art.
In the description of the present invention, it is to be understood that the terms "lateral", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "inner", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for the purpose of sub-description of the present invention and to simplify the description, but do not indicate or imply that the device or element referred to must have a particular orientation, be constructed in a particular orientation, and be operated, and thus should not be construed as limiting the present invention; furthermore, the terms "primary", "secondary" are used for descriptive purposes only and are not to be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated; thus, the definitions of "primary" and "secondary" are for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly including one or more of such features.
The totally-enclosed high-precision temperature and humidity independent control heat pump drying system comprises an outdoor component group A and an indoor component group B, wherein the outdoor component group A comprises a compressor A1, an outdoor heat exchanger A2, a liquid reservoir A3, a throttle valve A4 and a gas-liquid separator A5, the indoor component group B comprises a first indoor heat exchanger B1, a second indoor heat exchanger B2 and a plate-fin heat exchanger B3, and the first indoor heat exchanger B1 is installed in a plate-fin heat exchanger B3. Taking the airflow flowing direction as reference, the first indoor heat exchanger B1 and the plate-fin heat exchanger B3 are located in the upwind area of the airflow, the second indoor heat exchanger B2 is located in the downwind area, the first indoor heat exchanger B1 is connected between the air inlet pre-cooling channel B32 and the air outlet baffling channel B33 of the plate-fin heat exchanger B3, a gas-liquid separator A5 is arranged on the refrigerant input pipe a7 of the compressor A1, the refrigerant output pipe A6 of the compressor A1 is connected with the first input port a81 of the first four-way valve A8, one pipe of the second indoor heat exchanger B2 is connected with the first right output port a84 of the first four-way valve A8, two pipes are led out from the other pipe of the second indoor heat exchanger B2, the first pipe a9 is connected with the first electromagnetic switch valve a11, the second pipe a10 is connected with the first one-way valve a12 and the second input port a131 of the second four-way valve a13, the second indoor heat exchanger B39134 is connected with the first output port B1 of the second four-way valve a13, a third pipeline a14 led out from a second pipe orifice of the first indoor heat exchanger B1 is provided with a second electromagnetic switch valve a15, the first electromagnetic switch valve a11 and the second electromagnetic switch valve a15 are connected with each other and then are connected with a bridge circuit a16, and then are connected with a first connection port of the outdoor heat exchanger a2, the bridge circuit a16 is composed of four one-way valves, pipes led out from the first electromagnetic switch valve a11 and the second electromagnetic switch valve a15 are divided into two paths, each path is provided with a pair of one-way valves, a first pair of one-way valves a17 of the first path face to be opposite, a second pair of one-way valves a18 of the second path face back to back, one end of a refrigerant loopback bypass a19 is connected with a pipeline between the first pair of one-way valves a17, the other end is connected with a pipeline between the second pair of one-way valves a18, and a refrigerant accumulator A3 and a throttle 4 are sequentially connected on a bypass a19 of the bridge circuit a16 along the flow direction. The second connection port of the outdoor heat exchanger A2 is connected with the second left output port A132 of the second four-way valve A13, the first left output port A82 of the first four-way valve A8 is connected with the second one-way valve A20 firstly, and then is connected with the second pipeline A10 between the first one-way valve A12 and the second four-way valve A13, and the first middle output port A83 of the first four-way valve A8 and the second middle output port A133 of the second four-way valve A13 are communicated with each other and are connected with the inlet of the gas-liquid separator A5. The first indoor heat exchanger B1, the second indoor heat exchanger B2 and the outdoor heat exchanger a2 are all coil heat exchangers.
The first mode is as follows: heating and warming mode (as shown in figure 1)
This is the maximum heating mode, at which time the first four-way valve A8 is not energized, the first input port a81 of the first four-way valve A8 is connected to the first right output port a84, the first left output port a82 is connected to the first middle output port a83, the second four-way valve a13 is energized, at which time the second input port a131 of the second four-way valve a13 is connected to the second right output port a131, the second left output port a132 is connected to the second middle output port a133, the first solenoid switch valve a11 is closed, and the second solenoid switch valve a15 is open. The plate fin heat exchanger fan B31, the second indoor heat exchanger fan B21 and the outdoor heat exchanger fan a21 are all turned on. The flow path of the refrigerant is shown by the arrows in fig. 2 when the system is in operation.
The refrigerant flows out of the compressor A1, the refrigerant is in a high-temperature and high-pressure gas phase at the moment, the refrigerant firstly passes through the first four-way valve A8, the first four-way valve A8 is not electrified at the moment, the refrigerant enters from the first input port A81 of the first four-way valve A8, flows out from the first right output port A84 and then flows through the second indoor heat exchanger B2, and the second indoor heat exchanger B2 at the moment is equivalent to the action of a secondary condenser. And then, the refrigerant flows out of the second indoor heat exchanger B2 and flows to the second four-way valve A13, the refrigerant flows in from the second input port A131 of the second four-way valve A13, flows out from the second right output port A131 and then flows through the first indoor heat exchanger B1, the first indoor heat exchanger B1 is equivalent to a primary condenser, the refrigerant is changed into a low-temperature low-pressure liquid phase at the moment, and the air in the drying chamber absorbs heat from the two indoor heat exchangers in the process of sequentially flowing through the plate-fin heat exchanger B3, the first indoor heat exchanger B1 and the second indoor heat exchanger B2, so that the air in the drying chamber is rapidly heated and warmed, and the double heating mode is the most efficient heating mode for the air in the drying chamber. Next, after passing through the second electromagnetic switch valve a15, the refrigerant passes through the bridge circuit a16, passes through the accumulator A3 and the throttle valve a4, and then passes through the outdoor heat exchanger a2, where the outdoor heat exchanger a2 is equivalent to an evaporator, the refrigerant is evaporated into a gas phase in the outdoor heat exchanger a2, absorbs heat from the outside, and the refrigerant changed into the gas phase passes through the second left output port a132 and the second middle output port a133 of the second four-way valve a13, and finally passes through the gas-liquid separator a5 and returns to the compressor A1. Thus, according to the circulation, the air in the drying chamber is heated and heated rapidly. It should be noted that, since the refrigerant is in a low-pressure gas-liquid mixed state after passing through the second indoor heat exchanger B2 to remove heat, and the refrigerant passing through the outdoor heat exchanger a2 is in a high-pressure gas-phase state, when the refrigerant flows from the second four-way valve a13 to the gas-liquid separator a5, a part of the gaseous refrigerant also flows to the first four-way valve A8 and the second one-way valve a20, but due to the above reasons, the pressure in the closing direction of the second one-way valve a20 is much higher than the pressure in the opening direction, and therefore the second one-way valve a20 is not opened, that is, the path is blocked.
And a second mode: constant temperature dehumidification mode (as shown in fig. 2 and 3).
This mode is divided into two cases, one is overheating to trim the excess heat to maintain a constant temperature, and the other is supercooling warming to maintain a constant temperature.
In the first case: the superheat trimming adjusts the excess heat to maintain the refrigerant flow at a constant temperature (as shown in fig. 2).
At this time, neither the first four-way valve A8 nor the second four-way valve a13 is energized, the first solenoid switch valve a11 is closed, and the second solenoid switch valve a15 is opened, and in this state, the first input port a81 of the first four-way valve A8 communicates with the first right output port a84, the first left output port a82 communicates with the first middle output port a83, the second input port a131 of the second four-way valve a13 communicates with the second left output port a132, and the second right output port a131 communicates with the second middle output port a 133. The plate fin heat exchanger fan B31, the second indoor heat exchanger fan B21 and the outdoor heat exchanger fan a21 are all turned on. The flow path of the refrigerant is shown by the arrows in fig. 2 when the system is in operation.
After being delivered from the compressor A1, the refrigerant firstly flows through the first four-way valve A8 and flows out from the first right output port a84 of the first four-way valve A8, then flows through the second indoor heat exchanger B2 to dissipate heat (in this mode, the second indoor heat exchanger B2 is a primary condenser), that is, the high-temperature and high-pressure refrigerant is subjected to primary heat dissipation and condensation, that is, the air in the drying chamber is heated and warmed, then the refrigerant flows out from the second indoor heat exchanger B2, flows into the second input port a131 of the second four-way valve a13 after passing through the first check valve a12, and then flows out from the second left output port a132, and then the flowing-out refrigerant flows into the outdoor heat exchanger a2 to perform secondary heat dissipation (here, the outdoor heat exchanger a2 is a secondary condenser), that is further heat dissipation and condensation, and then flows through the bridge circuit a16, the accumulator A3 and the throttle valve a4 in turn after being secondarily condensed, and then flows into the first indoor heat exchanger B1 after passing through the second electromagnetic switch valve a15, the refrigerant is evaporated and gasified in the first indoor heat exchanger B1, the heat contained in the air flowing through the drying chamber can be absorbed in the process of evaporation and gasification of the refrigerant, namely, the air is refrigerated, at the moment, the air flowing through the plate-fin heat exchanger B3 and the first indoor heat exchanger B1 is rapidly cooled, the water vapor contained in the air is solidified into water drops and collected after the temperature of the air is reduced, so that the dehumidification treatment of the air in the drying chamber is completed, and the dehumidified air can flow through the subsequent second indoor heat exchanger B2 to be heated and heated. The refrigerant is discharged from the second indoor heat exchanger B2, flows into the second right output port a131 of the second four-way valve a13, flows out of the second middle output port a133, and finally flows through the gas-liquid separator a5 and returns to the compressor A1.
In this state, when the temperature in the drying chamber is too high, the fan a21 of the outdoor heat exchanger needs to be turned on, so that the outdoor air flowing through the outdoor heat exchanger a2 flows faster, the condensation efficiency is improved, the heat dissipation with large air volume can dissipate more heat of the refrigerant flowing through the outdoor heat exchanger a2, at this time, more refrigerants are converted from a gas phase to a liquid phase, the liquid phase content of the refrigerant is high, and the temperature is lower, the heat absorption efficiency of the refrigerant flowing into the first indoor heat exchanger B1 and evaporating into the gas phase is higher, and under the condition that the temperature of the drying chamber is not changed, the air in the drying chamber is cooled to be at a lower temperature when flowing through, so that the temperature of the drying chamber is reduced, and the air in the drying chamber is reduced to a set constant temperature value.
In the second case: the refrigerant flow state at a constant temperature is maintained by supercooling and raising the temperature (as shown in fig. 3).
The flow of the refrigerant in this state is the same as that in the first case, but when the temperature of the air in the drying chamber is too low, that is, the temperature in the drying chamber is lower than the set constant temperature value, at this time, in order to raise the temperature in the drying chamber to the constant temperature value, it is only necessary to turn off the outdoor heat exchanger fan a21, reduce the air flow of the fan, namely, the condensing efficiency of the exterior heat exchanger a2 is lowered, and at this time, the efficiency of the refrigerant changing from the gas phase to the liquid phase becomes low, i.e., the liquid phase content of the refrigerant is decreased and the temperature is not too low, the amount of heat absorbed by the refrigerant when the refrigerant is sent to the first indoor heat exchanger B1 to be evaporated is decreased, i.e., the cooling capacity, is reduced, so that the temperature of the drying chamber air passing through the first indoor heat exchanger B1 is not lowered too much, after the air is cooled and dehumidified by the first indoor heat exchanger B1, the air subsequently flows through the second indoor heat exchanger B2 to be heated and heated, and the temperature is increased to be higher, so that the temperature of the air in the drying chamber can be increased to a constant temperature value.
And a third mode: cooling dehumidification mode (as shown in fig. 4).
In this state, the first four-way valve A8 is energized, and the first input port a81 of the first four-way valve A8 is in communication with the first left output port a82, and the first right output port a84 is in communication with the first middle output port a 83. The second four-way valve a13 is de-energized and the second input port a131 of the second four-way valve a13 is in communication with the second left output port a132 and the second right output port a131 is in communication with the second middle output port a 133. The first electromagnetic opening/closing valve a11 is closed, and the second electromagnetic opening/closing valve a15 is opened. The plate fin heat exchanger fan B31, the second indoor heat exchanger fan B21 and the outdoor heat exchanger fan a21 are all turned on. The flow path of the refrigerant is shown by the arrows in fig. 4 when the system is in operation.
The refrigerant flows out of the compressor a1, first passes through the first input port a81 of the first four-way valve A8, flows out of the first left output port a82, then passes through the second check valve a20, and flows to the second four-way valve a13, where the refrigerant does not flow to the second indoor heat exchanger B2 due to the blockage of the first check valve a 12. The refrigerant flows in from the second input port a131 of the second four-way valve a13 and flows to the exterior heat exchanger a2 from the second left output port a132, the exterior heat exchanger a2 at this time serves as a condenser, the high-temperature and high-pressure refrigerant is cooled and cooled in the exterior heat exchanger a2 and is changed to a liquid phase, the refrigerant flowing out of the exterior heat exchanger a2 flows through the bridge circuit a16, the accumulator A3 and the throttle valve a4, then flows into the first indoor heat exchanger B1 after passing through the second electromagnetic switch valve A15, the refrigerant is evaporated and gasified in the first indoor heat exchanger B1, the air in the drying room flows into the plate-fin heat exchanger B3 in the gasification process and flows through the first indoor heat exchanger B1, when the drying chamber air passes through the first indoor heat exchanger B1, the drying chamber air is cooled and dehumidified, and the refrigerant flows out of the first indoor heat exchanger B1, flows into the second right output port a131 of the second four-way valve a13, flows out of the second middle output port a133, passes through the gas-liquid separator a5, and then flows back into the compressor A1. After the refrigerant flows out of the second four-way valve a13, the refrigerant does not flow to the first four-way valve A8 and the second indoor heat exchanger B2, because the air pressures at the two sides of the first check valve a12 are different, the air pressure at the outlet side of the first check valve a12 is the same as the air pressure at the outlet of the compressor a1, the refrigerants are high-temperature and high-pressure gas-phase refrigerants compressed by the compressor a1, and the air pressure at the input end of the first check valve a12 is the gas-phase refrigerant evaporated by the refrigerant in the first indoor heat exchanger B1, so the air pressure at the output end of the first check valve a12 is much higher than the air pressure at the input end, the evaporated refrigerant does not flow to the first four-way valve A8 and the second indoor heat exchanger B2, and the second indoor heat exchanger B2 of this mode does not participate in the operation. In order to increase the efficiency of the cooling and dehumidifying mode, the fan a21 of the outdoor heat exchanger is started to improve the condensing efficiency of the outdoor heat exchanger a2, so that more gas-phase refrigerant is converted into liquid-phase refrigerant. Therefore, in this mode, the outdoor heat exchanger a2 condenses the refrigerant efficiently, and the first indoor heat exchanger B1 evaporates and gasifies the refrigerant to absorb heat of the indoor air of the drying chamber efficiently. Therefore, the efficient cooling and dehumidifying treatment of the indoor air of the drying chamber can be realized.
And a fourth mode: maximum cooling mode (as shown in fig. 5).
In this state, the first four-way valve A8 is energized, and the first input port a81 of the first four-way valve A8 is in communication with the first left output port a82, and the first right output port a84 is in communication with the first middle output port a 83. The second four-way valve a13 is de-energized and the second input port a131 of the second four-way valve a13 is in communication with the second left output port a132 and the second right output port a131 is in communication with the second middle output port a 133. The first electromagnetic switch valve a11 is opened, the second electromagnetic switch valve a15 is closed, and the refrigerant does not flow through the plate-fin heat exchanger B3 and the first indoor heat exchanger B1. A big feature in this mode is that the plate-fin heat exchanger fan B31 is turned off, and both the second indoor heat exchanger fan B21 and the outdoor heat exchanger fan a21 are turned on. The flow path of the refrigerant is shown by the arrows in fig. 5 when the system is in operation.
The refrigerant flows out of the compressor a1, first passes through the first input port a81 of the first four-way valve A8, flows out of the first left output port a82, then passes through the second check valve a20, and flows to the second four-way valve a13, where the refrigerant does not flow to the second indoor heat exchanger B2 due to the blockage of the first check valve a 12. The refrigerant flows in from the second input port a131 of the second four-way valve a13 and flows to the outdoor heat exchanger a2 from the second left output port a132, at this time, the outdoor heat exchanger a2 serves as a condenser, the high-temperature and high-pressure refrigerant is cooled in the outdoor heat exchanger a2 and is converted to a liquid phase, the refrigerant flowing out of the outdoor heat exchanger a2 flows through the bridge circuit a16, the accumulator A3 and the throttle valve a4, and then flows into the second indoor heat exchanger B2 after passing through the first electromagnetic switch valve a11, at this time, the refrigerant on both sides of the first check valve a12 has a higher pressure than that on the left side due to the pressure on the right side, so that the refrigerant flowing to the second indoor heat exchanger B2 does not flow through the first check valve a12, the refrigerant is evaporated and gasified in the second indoor heat exchanger B2, and the air in the drying chamber does not flow through the plate fin heat exchanger B3 and the first indoor heat exchanger B1 because the fan B31 is in the gasification process is in a closed state, and the refrigerant flows out of the second indoor heat exchanger B2, flows in from a first right output port A84 of the first four-way valve A8, flows out from a first middle output port A83, flows through a gas-liquid separator A5, and then flows back to the compressor A1. After the refrigerant flows out of the first four-way valve A8, the refrigerant does not flow to the second four-way valve a13 and the first indoor heat exchanger B1 because the second electromagnetic switching valve a15 is in a closed state, and the refrigerant does not flow through the second four-way valve a13 and the first indoor heat exchanger B1. In order to increase the cooling and refrigerating efficiency, the fan A21 of the outdoor heat exchanger is started, the condensing efficiency of the outdoor heat exchanger A2 is improved, and more gas-phase refrigerants are converted into liquid phases. Therefore, in the mode, the outdoor heat exchanger A2 efficiently condenses the refrigerant, and the second indoor heat exchanger B2 evaporates and gasifies the refrigerant to efficiently cool and refrigerate the dried indoor air. Compared with the third mode, the air in the drying chamber is not heated by the heat exchange of the plate-fin heat exchanger B3, so that the indoor air flows through the second indoor heat exchanger B2 at a relatively low temperature for cooling and refrigerating.
For the mode three (cooling dehumidification mode) and the mode four (maximum refrigeration mode), in the cooling dehumidification mode, most of cold energy is converted into condensed water to be separated out due to the precooling and reheating functions of the plate-fin heat recoverer, and the dehumidification effect is good and the cooling effect is not obvious. In the maximum refrigeration mode, the dehumidification effect is much smaller than that of the dehumidification effect, namely the proportion of the cold quantity part for cooling the water vapor into the condensed water is small, so that the temperature reduction effect is more obvious.
Claims (6)
1. The utility model provides a totally closed high accuracy humiture independent control heat pump drying system, including outdoor part group and indoor part group, outdoor part group is including the compressor, outdoor heat exchanger, the reservoir, choke valve and vapour and liquid separator, indoor part group is including first indoor heat exchanger, second indoor heat exchanger and plate-fin heat exchanger, use the air current flow direction as the reference, first indoor heat exchanger is located the upwind district of air current, second indoor heat exchanger is located the downwind district, first indoor heat exchanger is connected between the inlet air precooling passageway and the air-out baffling passageway of plate-fin heat exchanger, be provided with vapour and liquid separator on the refrigerant input tube of compressor, its characterized in that: a refrigerant output pipe of the compressor is connected with a first input port of the first four-way valve, one pipeline of the second indoor heat exchanger is connected with a first right output port of the first four-way valve, two pipelines are led out from the other pipeline of the second indoor heat exchanger, the first pipeline is connected with a first electromagnetic switch valve, the second pipeline is sequentially connected with a first one-way valve and a second four-way valve, a second right output port of the second four-way valve is connected with a first pipe orifice of the first indoor heat exchanger, a third pipeline led out from a second pipe orifice of the first indoor heat exchanger is provided with a second electromagnetic switch valve, the first electromagnetic switch valve and the second electromagnetic switch valve are connected with each other and then connected with a first connecting port of the outdoor heat exchanger, a second connecting port of the outdoor heat exchanger is connected with a second left output port of the second four-way valve, the first left output port of the first four-way valve is connected with the second one-way valve, and then connected with a second pipeline between the first one-way valve and the second four-way valve, and a first middle output port of the first four-way valve and a second middle output port of the second four-way valve are communicated with each other and are connected with an inlet of the gas-liquid separator.
2. The fully-closed high-precision temperature and humidity independent control heat pump drying system according to claim 1, characterized in that: and a bridge type loop is arranged between the junction of the first electromagnetic switch valve and the second electromagnetic switch valve and the first connection port of the outdoor heat exchanger.
3. The fully-closed high-precision temperature and humidity independent control heat pump drying system according to claim 2, characterized in that: a liquid reservoir and a throttle valve are sequentially connected to the loop bypass of the bridge loop along the flowing direction of the refrigerant.
4. The fully-closed high-precision temperature and humidity independent control heat pump drying system according to claim 1, characterized in that: the first indoor heat exchanger, the second indoor heat exchanger and the outdoor heat exchanger are coil type heat exchangers.
5. The fully-closed high-precision temperature and humidity independent control heat pump drying system according to claim 2, characterized in that: the bridge circuit is composed of four one-way valves, pipes led from the first electromagnetic switch valve and the second electromagnetic switch valve are divided into two paths, each path is provided with a pair of one-way valves, the pair of one-way valves of the first path face to be opposite, and the pair of one-way valves of the second path face back to back.
6. The fully-closed high-precision temperature and humidity independent control heat pump drying system according to claim 3, characterized in that: the bridge-type loop is composed of four one-way valves, pipes led from the first electromagnetic switch valve and the second electromagnetic switch valve are divided into two paths, each path is provided with a pair of one-way valves, the pair of one-way valves of the first path face to face oppositely, the pair of one-way valves of the second path face back to back, one end of the loop-back bypass is connected with a pipeline between the two one-way valves of the first path, and the other end of the loop-back bypass is connected with a pipeline between the two one-way valves of the second path.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111551313.2A CN114034183A (en) | 2021-12-17 | 2021-12-17 | Totally-enclosed high-precision temperature and humidity independent control heat pump drying system |
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| CN202111551313.2A CN114034183A (en) | 2021-12-17 | 2021-12-17 | Totally-enclosed high-precision temperature and humidity independent control heat pump drying system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115289827A (en) * | 2022-07-19 | 2022-11-04 | 康特(苏州)能源环境设备有限公司 | Closed zero-humidity-discharge efficient heat pump drying device and drying method |
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2021
- 2021-12-17 CN CN202111551313.2A patent/CN114034183A/en not_active Withdrawn
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115289827A (en) * | 2022-07-19 | 2022-11-04 | 康特(苏州)能源环境设备有限公司 | Closed zero-humidity-discharge efficient heat pump drying device and drying method |
| CN115289827B (en) * | 2022-07-19 | 2023-09-22 | 康特(苏州)能源环境设备有限公司 | Closed type zero-wet-emission efficient heat pump drying device and drying method |
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Application publication date: 20220211 |