CN114111313A - Dehumidification drying heat pump system fusing compressor driving type quasi loop heat pipe - Google Patents
Dehumidification drying heat pump system fusing compressor driving type quasi loop heat pipe Download PDFInfo
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- CN114111313A CN114111313A CN202111413904.3A CN202111413904A CN114111313A CN 114111313 A CN114111313 A CN 114111313A CN 202111413904 A CN202111413904 A CN 202111413904A CN 114111313 A CN114111313 A CN 114111313A
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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
- 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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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
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Abstract
The invention relates to a dehumidification and drying heat pump system of a fusion compressor driving type quasi loop heat pipe, which comprises a refrigerant circulation flow path and an air flow path, wherein the refrigerant circulation flow path comprises a refrigerant flow path of a compressor, a condenser, a condensation reheating section, a throttle valve and an evaporator which are sequentially connected; the dehumidification drying heat pump system of the fusion compressor driving type simulated loop heat pipe also comprises an evaporation pre-cooling section which is connected into a refrigerant circulating flow path; the air flow path comprises a first air branch of an evaporation pre-cooling section, an evaporator, a condensation reheating section and a condenser which are sequentially connected, the evaporation pre-cooling section carries out pre-cooling return air, and the condensation reheating section carries out reheating return air. Compared with the prior art, the heat exchange of air fluid in front of and behind the evaporator is realized through the action of the compressor driving type simulated loop heat pipe, useless cold effect sensible heat carried by air at the inlet of the evaporator is reduced, and the latent heat ratio corresponding to dehumidification in the total refrigerating capacity is improved, so that the dehumidification capacity is improved, and the dehumidification efficiency is increased.
Description
Technical Field
The invention relates to a dehumidification and drying system of a vapor compression heat pump, in particular to a dehumidification and drying heat pump system integrating a compressor-driven pseudo loop heat pipe.
Background
The refrigeration heat pump circulating system can be used for replacing a traditional electric heating system, greatly reduces power consumption, and promotes energy conservation, emission reduction and carbon neutralization.
When the refrigeration heat pump circulating system is used for dehumidification, drying and other applications, compared with the modes of solution dehumidification, solid adsorption dehumidification and the like, the refrigeration heat pump circulating system has the advantages of compact structure, stable operation and convenient maintenance. However, the cooling and dehumidifying means adopted by the refrigeration heat pump circulating system needs to cool the air to a temperature lower than the dew point, and then the air is condensed to realize dehumidification. The sensible heat corresponding to the temperature of the part reduced to the dew point has no direct effect on dehumidification, and occupies a larger proportion of the total refrigerating capacity, so that the dehumidification performance of the system is influenced.
Patent CN112050618A discloses a triple effect heat recovery type mixes wind formula heat pump drying system, sets up the loop heat pipe through the evaporimeter that heats heat pump circulation system around, realizes the energy transfer between the air, utilizes the cold volume precooling of the air behind the evaporimeter cooling dehumidification of flowing through to get into the return air before the evaporimeter, makes the sensible heat that falls the dew point temperature in the total refrigerating output of evaporimeter and corresponds to account for the ratio and reduce, the latent heat that the dehumidification corresponds accounts for the ratio and increases to the dehumidification ability of system has been promoted.
The measures taken in the above patent improve the dehumidification effect of the evaporator but require the introduction of a separate loop heat pipe system. The loop heat pipe is used as a passive heat exchange system, is different from active heat exchange of a refrigeration heat pump system, lacks a direct driving means, needs to be self-driven by gravity and capillary force, and is often difficult to guarantee the actual application effect. If the refrigerant pump or other power components are used for driving, the cost is high and the economical efficiency is poor.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a dehumidification and drying heat pump system integrating a compressor driving type simulated loop heat pipe, wherein the compressor driving type simulated loop heat pipe means that a refrigerant in the system flows in two or more heat exchangers in a cycle under the power provided by a compressor, so that the effect of enhancing the heat conduction of fluid in the similar loop heat pipe is realized.
The vapor compression heat pump dehumidification drying system of the pseudo loop heat pipe can actively and controllably realize the effect similar to the loop heat pipe by driving the refrigerant to flow among the heat exchangers in the circulation through the compressor, and realize the heat exchange of the front air and the rear air of the evaporator.
The purpose of the invention can be realized by the following technical scheme:
the invention aims to protect a dehumidification drying heat pump system fusing a compressor driving type quasi loop heat pipe, which comprises a refrigerant circulation flow path and an air flow path, wherein the refrigerant circulation flow path comprises a refrigerant flow path of a compressor, a condenser, a condensation reheating section, a throttle valve and an evaporator which are sequentially connected;
the dehumidification drying heat pump system of the fusion compressor driving type simulated loop heat pipe also comprises an evaporation pre-cooling section which is connected into a refrigerant circulating flow path;
the air flow path comprises an evaporation pre-cooling section, an evaporator, a condensation reheating section and a first air branch of the condenser which are connected in sequence, namely the air flow path sequentially passes through the evaporation pre-cooling section, the evaporator, the condensation reheating section and an air channel of the condenser under the driving of a fan.
The evaporation pre-cooling section carries out pre-cooling air returning, and the condensation re-heating section carries out re-heating air returning, so that heat exchange of front and back air fluids of the evaporator is realized, useless cold effect sensible heat carried by air at the inlet of the evaporator is reduced, and finally the latent heat proportion corresponding to dehumidification in the total refrigerating capacity, namely the dehumidification proportion is improved.
Further, the output end of the evaporation precooling section refrigerant flow path is connected with a compressor.
Furthermore, the air flow path also comprises a second air branch which is branched out, the second air branch is directly bypassed to the front air inlet of the fan and uniformly mixed with the first air branch after the condensation reheating section and before the fan, and then flows through the condenser together, so that the air flow path is adapted to the large return air volume scene.
In one embodiment of the present disclosure, the refrigerant circulation flow path is branched into another branch after the outlet of the condensation reheating section, throttled by the auxiliary throttle valve, and then connected to the input end of the refrigerant flow path of the evaporation pre-cooling section.
Specifically, in the refrigerant circulation flow path: the two-phase refrigerant in the evaporator absorbs heat from the air flowing through and evaporates into superheated gas, and the superheated gas is sucked from the air suction port and is primarily compressed by the compressor; the two-phase refrigerant with higher saturation temperature in the evaporation pre-cooling section absorbs heat from the air flowing through and evaporates into superheated gas, is sucked by the compressor from the middle air supplement port, is mixed with the other refrigerant which is sucked from the outlet of the evaporator and is primarily compressed, and is compressed to higher condensation pressure again. The high-temperature and high-pressure refrigerant sequentially flows through the condenser and the condensation reheating section for condensation and supercooling, flows out of the condensation reheating section, is divided into two parts, is throttled by the throttle valve and the auxiliary throttle valve respectively, and then enters the evaporator and the evaporation precooling section to complete the refrigerant circulation.
Specifically, in the air flow path: the inlet air respectively flows through the primary cooling of the evaporation pre-cooling section, the deep dehumidification of the evaporator, the primary reheating of the condensation reheating section and the secondary reheating of the condenser and then is blown to the product to be dried. When being provided with the second air branch road, first air branch road is after the preliminary cooling of evaporation precooling section, evaporimeter degree of depth dehumidification, the preliminary reheat of condensation reheat section are flowed through respectively, and is mixed evenly with the direct bypass's of air inlet second air branch road, and the condenser that again together flows through is reheated to suitable stoving temperature by the secondary.
As an embodiment of the present invention, the refrigerant circulation flow path is divided into two sections after the compressor outlet:
one path of the refrigerant enters the evaporator after passing through the condenser and then is throttled by the throttle valve, and then enters the compressor;
the other path enters a refrigerant flow path of the condensation reheating section, is throttled by an auxiliary throttle valve and then enters a refrigerant flow path of the evaporation pre-cooling section.
The high-temperature high-pressure refrigerant at the outlet of the compressor is directly divided into two parts, wherein one part of the refrigerant is condensed by a condenser to release heat to flowing air, then the refrigerant is throttled by a throttle valve to reach a low saturation temperature and then enters an evaporator, and the refrigerant absorbs heat from the flowing air and is evaporated and then enters the compressor; the other path of the air enters a condensation reheating section for reheating flowing air, is throttled to a higher saturation temperature by an auxiliary throttle valve and then enters an evaporation pre-cooling section, absorbs heat from the flowing air for evaporation, and then enters a middle air supplement port of the compressor.
In one embodiment of the present invention, the condensing and reheating section and the condenser are combined in series, so as to complete the condensing and subcooling processes of the refrigerant at the same time.
As an embodiment of the present invention, the refrigerant circulation flow path is divided into two sections after the condenser:
one path of refrigerant flows through a condensing reheating section, is subcooled, throttled and then enters a refrigerant flow path of an evaporator;
the other path directly enters a refrigerant flow path of the evaporation pre-cooling section.
Further, the compressor adopts an enhanced vapor injection type compressor with a middle air supplement port or adopts a two-stage compression mode that two compressors are connected in series.
As a preferred embodiment of the technical scheme, the compressor adopts an enhanced vapor injection compressor with a middle air supplement port;
after the refrigerant circulating flow passes through the condenser and the condensation reheating section, one path of refrigerant is throttled to a first saturation temperature by the throttle valve and then enters the evaporator, absorbs heat from flowing air and evaporates, and then enters the compressor;
and the other path of air enters an evaporation pre-cooling section after being throttled to a second saturation temperature by an auxiliary throttle valve, absorbs heat from flowing air and evaporates, and then enters a middle air supplement port of the compressor, wherein the second saturation temperature is higher than the first saturation temperature.
As a preferred embodiment of the technical scheme, the compressor adopts an enhanced vapor injection compressor with a middle air supplement port;
one path of the refrigerant circulating flow path is condensed by a condenser to emit heat to air flowing through, then is throttled by a throttle valve to a first saturation temperature and then enters an evaporator, absorbs heat from the air flowing through and evaporates, and then enters a compressor;
the other path of the air enters a condensation reheating section for reheating flowing air, is throttled to a second saturation temperature by an auxiliary throttle valve and then enters an evaporation pre-cooling section, absorbs heat from the flowing air, evaporates and then enters a middle air supplement port of the compressor, and the second saturation temperature is higher than the first saturation temperature.
The evaporation pre-cooling section and the condensation reheating section are fused in a refrigerant loop of the vapor compression heat pump, the liquidity of the evaporation pre-cooling section and the condensation reheating section is ensured by the driving of a compressor, the function similar to a loop heat pipe is substantially realized, and the heat exchange of front air fluid and rear air fluid of an evaporator is realized. For the evaporator with the deep dehumidification function, the inlet air is fully pre-cooled and then enters the evaporator to be dehumidified, the latent heat corresponding to dehumidification in the total refrigerating capacity is increased, and the dehumidification capacity and the dehumidification efficiency are improved under the same power consumption.
Compared with the prior art, the invention has the following advantages and beneficial effects:
1. the front and the back of an evaporator in the system are respectively provided with an evaporation pre-cooling section and a condensation reheating section, wherein the evaporation pre-cooling section is used for pre-cooling return air, the condensation reheating section is used for reheating return air (recovering the cold energy of the return air), the cooperation of the evaporation pre-cooling section and the condensation reheating section substantially plays a role similar to a loop heat pipe, the heat exchange of air fluid in the front and the back of the evaporator is realized, the useless cold effect sensible heat carried by air at the inlet of the evaporator is reduced, the latent heat ratio corresponding to dehumidification in the total refrigerating capacity is improved, the dehumidification capacity is improved, and the dehumidification efficiency is increased.
2. The pseudo-loop heat pipe is fused in the refrigerant circulation of the active heat exchange vapor compression heat pump, and compared with capillary force or gravity driving of independently setting the loop heat pipe, the driving force of the compressor is stronger, the good fluidity of the refrigerant in the pseudo-loop heat pipe is ensured, and the heat exchange effect is further enhanced. The application bottleneck that the passive heat exchange effect of the traditional independent loop heat pipe is difficult to guarantee is overcome.
3. The loop heat pipe is fused into a refrigerant loop of the vapor compression heat pump, the integral structure is simpler and more compact, and the design is easy to realize.
Drawings
Fig. 1 is a schematic structural diagram of a system according to embodiment 1 of the present invention.
FIG. 2 is a graph of pressure-enthalpy values (p-h graph) of example 1 of the present invention.
Fig. 3 is a schematic structural diagram of a system according to embodiment 2 of the present invention.
FIG. 4 is a pressure-enthalpy graph (p-h graph) according to example 2 of the present invention.
Fig. 5 is a schematic structural diagram of a system according to embodiment 3 of the present invention.
Fig. 6 is a schematic structural diagram of a system according to embodiment 4 of the present invention.
Figure 7 is a refrigeration heat pump circulation system with loop heat pipe disclosed in patent CN 112050618A.
In the figure: 1. the system comprises a compressor, 2, a condenser, 3, a condensation reheating section, 4, a throttle valve, 5, an evaporator, 6, an auxiliary throttle valve, 7, an evaporation pre-cooling section, 8, a fan, 9, air inlet, 10, a first air branch, 11, a second air branch, 12, air supply, 13, a loop heat pipe evaporation side, 14 and a loop heat pipe condensation side.
Detailed Description
The invention is described in detail below with reference to the figures and specific embodiments.
Example 1
In the embodiment, referring to fig. 1, the dehumidifying and drying heat pump system incorporating a compressor-driven pseudo loop heat pipe mainly includes a compressor 1, a condenser 2, a condensation reheating section 3, a throttle valve 4, an evaporator 5, an auxiliary throttle valve 6, an evaporation precooling section 7 and a fan 8.
The embodiment adopts an enhanced vapor injection compressor 1 with a middle air supplement port or adopts a two-stage compression mode that two compressors are connected in series.
In the embodiment, the refrigerant flowing out of the condensation reheating section 3 is divided into two parts, wherein one part of the refrigerant is throttled by the throttle valve 4 to reach a lower saturation temperature and then enters the evaporator 5, and the refrigerant absorbs heat from flowing air and is evaporated and then enters the compressor 1; the other path of the air is throttled to a higher saturation temperature by an auxiliary throttle valve 6 and then enters an evaporation pre-cooling section 7, absorbs heat from flowing air and evaporates, and then enters a middle air supplement port of the compressor 1.
The embodiment also comprises an air flow path, under the drive of the fan 8, the inlet air 9 is divided into two parts, wherein a first air branch 10 sequentially flows through the evaporation pre-cooling section 7, the evaporator 5 and the condensation re-heating section 3; the second air branch 11 is a bypass branch of the inlet air 9, and is mixed with the air flowing out of the air channel of the condensation reheating section 3 by the first air branch 10, and then flows through the condenser 2 together.
In the present embodiment, a dehumidification and drying heat pump system incorporating a compressor-driven pseudo loop heat pipe is shown in fig. 1 and fig. 2, and a refrigerant circulation flow process is as follows: the two-phase refrigerant in the evaporator 5 absorbs heat from the air flowing therethrough and evaporates into superheated gas (state I to state a), is sucked from the suction port by the compressor 1 and is preliminarily compressed (state a to state B); the higher saturation temperature two-phase refrigerant in the evaporating pre-cooling section 7 also absorbs heat from the air flowing therethrough and evaporates into a superheated gas (state G to state H), is sucked in from the intermediate supplementary air port by the compressor 1, is mixed with another refrigerant (state H and state B are mixed to state C) sucked in from the outlet of the evaporator 5 and preliminarily compressed, and is compressed again to a higher condensing pressure (state C to state D). The high-temperature and high-pressure refrigerant then flows through the condenser 2 and the condensation reheating section 3 for condensation and supercooling (the state D is from E to the state F), flows out of the condensation reheating section 3, is divided into two parts, is throttled by the throttle valve 4 and the auxiliary throttle valve 6 respectively (the state F is from the state F to the state I and the state G), and enters the evaporator 5 and the evaporation precooling section 7 to complete the refrigerant circulation.
The embodiment of the invention provides a dehumidification drying heat pump system integrating a compressor driving type simulated loop heat pipe, and the air flow process is as follows: under the drive of a fan 8, an inlet air 9 is divided into two branches, wherein a first air branch 10 respectively flows through an evaporation pre-cooling section 7 for primary cooling, an evaporator 5 for deep dehumidification and a condensation reheating section 3 for primary reheating; the second air branch 11 is directly bypassed, mixed with the air flowing out from the air channel of the condensation reheating section 3 by the first air branch 10, and then flows through the condenser 2 together to be reheated to a proper drying temperature.
The evaporation pre-cooling section 7 and the condensation reheating section 3 in the embodiment form a compressor-driven pseudo loop heat pipe, are fused in a refrigerant loop of the vapor compression heat pump, and have the liquidity ensured by the driving of the compressor 1, thereby playing the role similar to the loop heat pipe. The evaporation pre-cooling section 7 is equal to the evaporation end of the loop heat pipe and used for pre-cooling the air entering the evaporator 5, and the condensation re-heating section 3 is equal to the condensation end of the loop heat pipe and used for re-heating the air flowing out of the air channel of the evaporator 5, so that the heat exchange of air fluid before and after the evaporator 5 is realized. For the evaporator 5 with the deep dehumidification function, the inlet air is fully pre-cooled and then enters the evaporator 5 to be dehumidified, the latent heat corresponding to dehumidification in the total refrigerating capacity is increased, and the dehumidification capacity and the dehumidification energy efficiency are improved under the same power consumption.
Example 2
The dehumidifying and drying heat pump system combining the compressor driving type pseudo loop heat pipe in the present embodiment, referring to fig. 3, is mainly different from embodiment 1 in the arrangement of the refrigerant flow path.
In the embodiment, a high-temperature and high-pressure refrigerant at the outlet of a compressor 1 is directly divided into two parts, wherein one part of the refrigerant is condensed by a condenser 2 to release heat to flowing air, then is throttled by a throttle valve 4 to reach a low saturation temperature and then enters an evaporator 5, absorbs heat from the flowing air and evaporates, and then enters the compressor 1; the other path of the air enters a condensation reheating section 3 for reheating flowing air, is throttled to a higher saturation temperature by an auxiliary throttle valve 6 and then enters an evaporation precooling section 7, absorbs heat from the flowing air and evaporates, and then enters an intermediate air supplement port of the compressor 1.
Referring to fig. 3 and 4, the refrigerant circulation flow process of the present embodiment is as follows: the two-phase refrigerant in the evaporator 5 absorbs heat from the air flowing therethrough and evaporates into superheated gas (state I to state a), is sucked from the suction port by the compressor 1 and is preliminarily compressed (state a to state B); the higher saturation temperature two-phase refrigerant in the evaporating pre-cooling section 7 also absorbs heat from the air flowing therethrough and evaporates into a superheated gas (state G to state H), is sucked in from the intermediate supplementary air port by the compressor 1, is mixed with another refrigerant (state H and state B are mixed to state C) sucked in from the outlet of the evaporator 5 and preliminarily compressed, and is compressed again to a higher condensing pressure (state C to state D). The high-temperature and high-pressure refrigerant is divided into two parts, one part of the refrigerant is condensed and supercooled (from a state D to a state E) by the condenser 2, and enters the evaporator 5 for continuous evaporation after being throttled by the throttle valve 4 (from the state E to the state I); the other path is condensed and supercooled (from a state D to a state F) by a condensation reheating section 3, throttled by an auxiliary throttle valve 6 (from the state F to a state G) and enters an evaporation precooling section 7 for continuous evaporation.
The evaporation pre-cooling section 7 and the condensation re-heating section 3 in the present example work together, which is equivalent to arranging loop heat pipes before and after the evaporator 5 (refer to fig. 7). The evaporation pre-cooling section 7 is equal to the evaporation end of the loop heat pipe and used for pre-cooling the air entering the evaporator 5, and the condensation reheating section 3 is equal to the condensation end of the loop heat pipe and used for reheating the air flowing out of the air channel of the evaporator 5. Therefore, the evaporation pre-cooling section 7 and the condensation reheating section 3 form a compressor driving type pseudo-loop heat pipe and are fused in a refrigerant loop of the vapor compression heat pump, the liquidity of the heat pipe is ensured by the driving of the compressor 1, the heat pipe has the effect similar to the loop heat pipe, and the heat exchange of air fluid in front of and behind the evaporator 5 is realized.
Example 3
The structure of the embodiment is schematically shown in fig. 5, and the basic principle is consistent with that of embodiment 1. Compared with the embodiment 1, the air flow path in the embodiment does not have the second air branch 11 for bypassing the mixed air, so the condensation reheating section 3 in the embodiment 1 can be combined with the condenser 2, and the condensation and supercooling of the refrigerant are all completed in the condenser 2 (the end of the refrigerant channel of the condenser 2 is a supercooling section). At this time, the evaporation pre-cooling section 7 and the refrigerant supercooling section in the condenser 2 form a compressor-driven pseudo loop heat pipe, and the heat exchange effect of the front air and the rear air of the evaporator 5 is realized. The form has compact structure and high component integration level, and is very suitable for application scenes with limited installation space.
Example 4
The structure of the embodiment is schematically shown in fig. 6, and the basic principle is consistent with that of embodiment 1. The difference is that in example 1, after all the refrigerant is subcooled in the condenser 2 and the condensation reheating section 3, it is throttled to a lower saturation temperature and an intermediate saturation temperature, respectively, into the evaporator 5 and the evaporation precooling section 7. In the embodiment, the refrigerant flow path is divided into two parts after the condenser 2, wherein one part of the refrigerant flow path passes through the condensation reheating section 3, is subcooled and throttled to a lower saturation temperature, and enters the evaporator 5; the other path enters an evaporation pre-cooling section 7 after being directly throttled without being cooled. In this embodiment, the branch that is throttled directly without cooling entails a larger throttling loss than in embodiment 1; but the other branch passes through the branch throttled after the condensation reheating section 3, and because the mass of the refrigerant is reduced, a larger supercooling degree can be generated, and the refrigerating capacity and the dehumidifying capacity in the evaporator 5 are further increased. The present embodiment is thus another configuration that balances the effects of the two branches.
Comparative example 1
Figure 7 is a schematic diagram of an equivalent system structure disclosed in patent CN112050618A, in which the loop heat pipe and the vapor compression heat pump cycle are both independent systems. The loop heat pipe comprises an evaporation side 13 and a condensation side 14, and the refrigeration heat pump circulating system comprises a compressor 1, a condenser 2, a condensation reheating section 3, a throttle valve 4 and an evaporator 5.
Compared with the prior art, the system directly fuses a pseudo loop heat pipe in the refrigerant cycle of the active heat exchange vapor compression heat pump, the front and the back of the evaporator 5 are respectively provided with an evaporation pre-cooling section 7 and a condensation reheating section 3, wherein the evaporation pre-cooling section 7 is used for pre-cooling return air, and the condensation reheating section 3 is used for reheating return air (recovering the cold energy of the return air), the two sections are similar to the evaporation side 13 and the condensation side 14 of the loop heat pipe in the figure 7, but the enhancement effect of the actual heat exchange effect is obviously improved, the system is matched with the loop heat pipe to substantially play the role of the loop heat pipe, the heat exchange of air fluid in the front and the back of the evaporator 5 is realized, the useless cold effect sensible heat carried by the inlet air of the evaporator 5 is reduced, the dehumidification capacity is improved, and the dehumidification energy efficiency is increased.
More importantly, compared with the traditional method that the loop heat pipe is independently arranged and driven by capillary force or gravity, the invention has stronger driving force of the compressor, ensures the good fluidity of the refrigerant in the pseudo-loop heat pipe and further enhances the heat exchange effect. The application bottleneck that the passive heat exchange effect of the traditional independent loop heat pipe is difficult to guarantee is overcome.
The embodiments described above are described to facilitate an understanding and use of the invention by those skilled in the art. It will be readily apparent to those skilled in the art that various modifications to these embodiments may be made, and the generic principles described herein may be applied to other embodiments without the use of the inventive faculty. Therefore, the present invention is not limited to the above embodiments, and those skilled in the art should make improvements and modifications within the scope of the present invention based on the disclosure of the present invention.
Claims (10)
1. A dehumidification drying heat pump system of a fusion compressor driving type pseudo loop heat pipe comprises a refrigerant circulation flow path and an air flow path, and is characterized in that the refrigerant circulation flow path comprises a refrigerant flow path of a compressor (1), a condenser (2), a condensation reheating section (3), a throttle valve (4) and an evaporator (5) which are connected in sequence;
the dehumidification drying heat pump system of the fusion compressor driving type simulated loop heat pipe also comprises an evaporation pre-cooling section (7) connected into a refrigerant circulating flow path;
the air flow path comprises an evaporation pre-cooling section (7), an evaporator (5), a condensation re-heating section (3) and a first air branch (10) of the condenser (2) which are connected in sequence;
the evaporation pre-cooling section (7) performs pre-cooling air return, and the condensation re-heating section (3) performs re-heating air return, so that heat exchange of front and back air fluids of the evaporator (5) is realized, useless cooling effect sensible heat carried by air at the inlet of the evaporator (5) is reduced, and the latent heat proportion corresponding to dehumidification in the total refrigerating capacity is finally improved.
2. The dehumidifying and drying heat pump system fusing the compressor driving type pseudo loop heat pipe as claimed in claim 1, wherein the output end of the refrigerant flow path of the evaporating pre-cooling section (7) is connected with the compressor (1).
3. The dehumidifying and drying heat pump system fusing the compressor driving type pseudo loop heat pipe as claimed in claim 1, wherein the air flow path further comprises a branched second air branch (11), the second air branch is directly bypassed to the front air inlet of the fan (8), and flows through the condenser (2) together with the first air branch (10) after being uniformly mixed after the condensation reheating section (3) and before the fan (8), so as to adapt to a large return air volume scene of the air flow path.
4. The dehumidifying and drying heat pump system fusing the compressor driving type pseudo loop heat pipe as claimed in claim 2 or 3, wherein the refrigerant circulation flow path is branched after the outlet of the condensation reheating section (3), throttled by the auxiliary throttle valve (6), and then connected with the refrigerant flow path input end of the evaporation precooling section (7).
5. The dehumidifying and drying heat pump system fusing the compressor driving type pseudo loop heat pipe as claimed in claim 2 or 3, wherein the refrigerant circulation flow path is divided into two after the outlet of the compressor (1):
one path of the refrigerant passes through the condenser (2), is throttled by the throttle valve (4), enters the evaporator (5) and then enters the compressor (1);
the other path enters a refrigerant flow path of the condensation reheating section (3), is throttled by an auxiliary throttle valve (6) and then enters a refrigerant flow path of the evaporation precooling section (7).
6. The heat pump system for dehumidifying and drying of a pseudo loop heat pipe driven by a combined compressor as claimed in claim 2, wherein the condensing and reheating section (3) and the condenser (2) are combined in series in a structure, thereby performing the condensing and subcooling processes of the refrigerant at the same time.
7. The dehumidifying and drying heat pump system fusing the compressor driving type pseudo loop heat pipe as set forth in claim 2, wherein the refrigerant circulation flow path is divided into two after the condenser (2):
one path of refrigerant flows through the condensation reheating section (3), is subcooled, throttled and then enters a refrigerant flow path of the evaporator (5);
the other path directly enters a refrigerant flow path of the evaporation pre-cooling section (7).
8. The dehumidifying and drying heat pump system fusing the compressor driving type pseudo loop heat pipe as claimed in claim 1, wherein the compressor (1) adopts an enhanced vapor injection type compressor with a middle air supplement port or a two-stage compression form with two compressors connected in series.
9. The dehumidifying and drying heat pump system fusing the compressor driving type pseudo loop heat pipe is characterized in that the compressor (1) adopts an enhanced vapor injection type compressor with a middle air supplement port;
after the refrigerant circulating flow passes through the condenser (2) and the condensation reheating section (3), one path of refrigerant is throttled to a first saturation temperature by the throttle valve (4) and then enters the evaporator (5), absorbs heat from flowing air and evaporates, and then enters the compressor (1);
and the other path of air is throttled to a second saturation temperature by an auxiliary throttle valve (6) and then enters an evaporation pre-cooling section (7), the air flowing through the air enters an intermediate air supplement port of the compressor (1) after absorbing heat and evaporating, and the second saturation temperature is higher than the first saturation temperature.
10. The dehumidifying and drying heat pump system fusing the compressor driving type pseudo loop heat pipe is characterized in that the compressor (1) adopts an enhanced vapor injection type compressor with a middle air supplement port;
one path of the refrigerant circulating flow path is condensed by a condenser (2) to emit heat to air flowing through, is throttled by a throttle valve (4) to a first saturation temperature, then enters an evaporator (5), absorbs heat from the air flowing through, evaporates and then enters a compressor (1);
the other path of the air enters a condensation reheating section (3) for condensation to reheat flowing air, then is throttled to a second saturation temperature by an auxiliary throttle valve (6) and then enters an evaporation precooling section (7), and the air absorbing heat and evaporating from the flowing air enters an intermediate air supplementing port of the compressor (1), wherein the second saturation temperature is higher than the first saturation temperature.
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