CN115218299A - Ultra-high energy efficiency dehumidifier for cutting off thermal bridge connection between supercooling section and condensing section fin - Google Patents
Ultra-high energy efficiency dehumidifier for cutting off thermal bridge connection between supercooling section and condensing section fin Download PDFInfo
- Publication number
- CN115218299A CN115218299A CN202210676911.0A CN202210676911A CN115218299A CN 115218299 A CN115218299 A CN 115218299A CN 202210676911 A CN202210676911 A CN 202210676911A CN 115218299 A CN115218299 A CN 115218299A
- Authority
- CN
- China
- Prior art keywords
- section
- evaporator
- supercooling
- refrigerant
- condenser
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000004781 supercooling Methods 0.000 title claims abstract description 106
- 238000005520 cutting process Methods 0.000 title claims abstract description 13
- 239000003507 refrigerant Substances 0.000 claims abstract description 131
- 238000009833 condensation Methods 0.000 claims abstract description 46
- 230000005494 condensation Effects 0.000 claims abstract description 46
- 238000013021 overheating Methods 0.000 claims abstract description 16
- 238000003303 reheating Methods 0.000 claims abstract description 6
- 230000009471 action Effects 0.000 claims description 4
- 238000001816 cooling Methods 0.000 abstract description 8
- 239000007788 liquid Substances 0.000 description 33
- 238000007791 dehumidification Methods 0.000 description 19
- 238000012546 transfer Methods 0.000 description 13
- 238000010586 diagram Methods 0.000 description 11
- 239000012530 fluid Substances 0.000 description 10
- 238000001704 evaporation Methods 0.000 description 8
- 230000008020 evaporation Effects 0.000 description 8
- 230000000694 effects Effects 0.000 description 7
- 230000006872 improvement Effects 0.000 description 7
- 238000005057 refrigeration Methods 0.000 description 7
- 239000012071 phase Substances 0.000 description 6
- 238000005516 engineering process Methods 0.000 description 5
- 239000007791 liquid phase Substances 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 230000008859 change Effects 0.000 description 4
- 230000005514 two-phase flow Effects 0.000 description 4
- 238000009834 vaporization Methods 0.000 description 4
- 230000008016 vaporization Effects 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Chemical compound O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 239000003814 drug Substances 0.000 description 2
- 235000013305 food Nutrition 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 241000208125 Nicotiana Species 0.000 description 1
- 235000002637 Nicotiana tabacum Nutrition 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000012809 cooling fluid Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007123 defense Effects 0.000 description 1
- 238000007689 inspection Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005549 size reduction Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/30—Arrangement or mounting of heat-exchangers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F2003/144—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only
- F24F2003/1446—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only by condensing
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Drying Of Gases (AREA)
Abstract
The invention provides an ultra-high energy efficiency dehumidifier for cutting off the thermal bridge connection between a supercooling section and a fin of a condensation section, which comprises the following components: the two-unit combined module comprises a condenser and an evaporator, and the condenser comprises an overheating heat release section, a condensation section and a supercooling section; the evaporator, the supercooling section and the condensing section are sequentially arranged in parallel, and refrigerant pipelines of the overheating heat release section, the condensing section and the supercooling section are sequentially connected in series; the inner diameter of the refrigerant pipeline of the supercooling section is smaller than that of the refrigerant pipeline of the condensation section; the output end of the supercooling section of the condenser is communicated with the input end of the evaporator through a throttling device; the fan is used for leading the main airflow at the inlet of the dehumidifier to firstly pass through the evaporator for cooling and dehumidifying, then sequentially pass through the supercooling section and the condensation section of the condenser for reheating for two times, and finally be discharged by the fan; the input end of the two-unit combination module is communicated with the output end of the compressor, and the output end of the two-unit combination module is communicated with the input end of the compressor to form a refrigerant circulation channel.
Description
Technical Field
The invention belongs to the technical field of dehumidifiers, and particularly relates to an ultra-high energy efficiency dehumidifier for cutting off connection between a supercooling section and a condensation section fin heat bridge.
Background
The working principle of the steam compression type dehumidifier is that the temperature of the humid air is reduced to be lower than the dew point temperature by utilizing the evaporator of the steam compression type refrigerating system, so that the water vapor in the air flowing through the evaporator is released, condensed and separated out, the water vapor component in the air is reduced, and the purpose of reducing the absolute moisture content of the air is achieved.
The dehumidifier is widely used in manufacturing workshops of electronic products, precision instruments and food and medicine, and special places such as audio-video rooms, libraries, archive rooms, inspection and quarantine rooms, computer rooms, laboratories, equipment rooms, telecommunication rooms, banks, operating rooms, tobacco warehouses, civil air defense engineering, military warehouses, food, medicine, seed warehouses and the like. In recent years, with the modernization of industrial business and the continuous improvement of living standard of people, commercial and household dehumidifiers show vigorous business opportunities, rapidly enter warehouses of factory workshops, offices and general family habitable rooms, and create more comfortable working and living environments for people.
The dehumidifier which is mainstream in the market at present has the advantages of simple structure, low price, reliable operation and easy maintenance. However, the following technical problems also exist:
for example, a patent application with the application number of 201711417767.4 and the name of dehumidifier, which is filed by refrigeration equipment limited in Guangdong America on 2017, 12 and 22 months, is published by the national intellectual property office, please refer to FIG. 1, and the dehumidifier has the technical idea of implementing the large wind volume of the condenser to reduce the condensation pressure and the compression work; however, due to the thermal bridge function of the fins of the lower condenser 2, that is, the heat conduction of the "refrigerant gas condensation area" in the lower condenser 2 to the "refrigerant liquid supercooling area" through the fin group, the supercooling degree of the refrigerant liquid at the tail end of the condenser is obviously insufficient, and the technical goal of implementing the "deep supercooling" of the condensate liquid by using the low-temperature air outlet of the evaporator is not realized.
For another example, the application number 201510117040.9 filed by shanghai berber culvert thermal energy science and technology limited on 17.03.2015 for the patent application entitled high-efficiency dehumidifier is 201510117040.9, please refer to fig. 2, the dehumidifier embeds the evaporator into the condenser composed of the condenser 1, the condenser 2 and the condenser 3, so that two technical goals of reducing the condensing pressure of the condenser large-air-volume evaporator by small air volume and improving the condensate supercooling degree by cooling the tail end of the condenser by low-temperature air outlet of the evaporator are achieved, and high-efficiency dehumidification is perfectly presented. But also has the problems that the low-temperature air outlet of the evaporator is only used for supercooling the condensate at the tail end of the condenser and does not participate in heat absorption of the main condensation phase-change section, and the sectional area of the air channel occupied by the main condensation phase-change section is too large, so that the whole structure of the dehumidifier is larger.
For another example, the application number of 201710940612.2 and the name of the invention of an invention of a dehumidifier, which are filed by the Fushan City West Bao electric Limited company in 2017, 09 and 30 are patent applications, please refer to fig. 3, the dehumidifier establishes an operation mode of a condenser large air volume evaporator small air volume, cuts off the connection between the condenser 3 and a fin heat bridge of a condenser 2 serving as a main condensation area of a refrigerant, blocks the heat transfer of the condensation area to a supercooling section through a fin group, and is beneficial to realizing the technical goal of deep supercooling high-efficiency dehumidification; however, the supercooling section of the patent application adopts a tube-fin heat exchanger with the same diameter as the main condensation section, and has the problems of low flow velocity of refrigerant liquid in the tube, low Reynolds number and low convection heat transfer coefficient at the inner side of the tube.
Disclosure of Invention
In order to solve the problems, the invention provides an ultra-high energy efficiency dehumidifier for cutting off the thermal bridge connection between a supercooling section and a fin of a condensation section, which comprises the following steps:
the two-unit combined module comprises a condenser and an evaporator, wherein the condenser comprises an overheating heat release section, a condensation section and a supercooling section (the overheating heat release section is a first stage and is also the front end of the condenser; the condensation section is a second stage and is also the middle section of the condenser; the supercooling section is a third stage and is also the tail end of the condenser, and the three stages are all heat release), and the overheating heat release section, the condensation section, the supercooling section and the evaporator are all fin tube type heat exchangers; the evaporator, the supercooling section and the condensing section are sequentially arranged in parallel, and refrigerant pipelines of the overheating heat release section, the condensing section and the supercooling section are sequentially connected in series; the inner diameter of the refrigerant pipeline of the supercooling section is smaller than that of the refrigerant pipeline of the condensation section; the output end of the supercooling section of the condenser is communicated with the input end of the evaporator through a throttling device;
the main air flow at the inlet of the dehumidifier firstly passes through the evaporator to reduce the temperature and dehumidify under the suction action of the fan, then sequentially passes through the supercooling section and the condensing section of the condenser to implement twice reheating, and finally is discharged by the fan;
the input end of the two-unit combination module is communicated with the output end of the compressor, and the output end of the two-unit combination module is communicated with the input end of the compressor to form a refrigerant circulation channel; the input end of the two combined modules is the input end of the overheat heat release section of the condenser, and the output end of the two combined modules is the output end of the evaporator.
Preferably, the evaporator is embedded in the condenser.
Preferably, the superheating heat release section is positioned above or below the evaporator or/and the supercooling section or/and the condensing section. If the superheating heat release section is positioned below the evaporator or/and the supercooling section or/and the condensing section, the drainage of the evaporator is affected. Therefore, it is preferable that the superheating heat release section is located above the evaporator or/and the subcooling section or/and the condensing section. Because the compressor exhaust pipe is arranged at the top, the compressor exhaust pipe is also conveniently connected with the compressor exhaust pipe. As an embodiment, the overheating heat release section and the condensation section are integrated, and the overheating heat release section is located above the condensation section, namely, the upper section of the same finned tube heat exchanger is the overheating heat release section, and the lower section of the same finned tube heat exchanger is the condensation section; as another embodiment, a superheating heat release section is separated from a condensing section, and the superheating heat release section is positioned above the evaporator, the supercooling section and the condensing section which are arranged side by side.
Preferably, the refrigerant pipes of the superheating heat release section, the condensation section and the evaporator have the same inner diameter.
Preferably, the inner diameter of the refrigerant pipeline of the condensation section is 9mm, and the inner diameter of the refrigerant pipeline of the supercooling section is not more than 7mm.
Preferably, the inner diameter of the refrigerant pipeline of the condensation section is 7mm, and the inner diameter of the refrigerant pipeline of the supercooling section is not more than 5mm.
Preferably, the refrigerant pipelines of the superheating heat release section, the condensing section, the supercooling section and the evaporator are sequentially connected in series, and an output port of the refrigerant pipeline of the supercooling section is communicated with an input port of the refrigerant pipeline of the evaporator through the throttling device.
Preferably, the refrigerant pipeline of the evaporator comprises at least two refrigerant sub-pipelines connected in parallel, and the output port of the refrigerant pipeline of the supercooling section is respectively communicated with the input ports of the refrigerant sub-pipelines through the throttling device.
Preferably, the fan is located at a side close to the condenser.
Preferably, the ultra-high energy efficiency dehumidifier for cutting off the connection between the supercooling section and the fin heat bridge of the condensation section further comprises a shell, wherein the two combined modules, the fan and the compressor are all arranged in the shell;
the shell is provided with the inlet and the outlet, the air inlet of the evaporator faces the inlet, and the air outlet of the fan faces the outlet.
Compared with the prior art, the invention has the following technical effects:
(1) implementing deep subcooling at higher levels
The tail end of the condenser adopts the thin-diameter finned tube heat exchanger, so that the flow velocity and Reynolds number of the refrigerant at the tail end of the condenser and the convective heat transfer coefficient of the refrigerant at the inner side of the tube are improved, and the heat release effect of the refrigerant condensate on low-temperature air outlet of the evaporator is improved; the heat transfer technology of the fin heat bridge between the high-temperature condensation section and the tail end supercooling section in the condenser is combined and cut off, the heat transfer technology of the condensation section to the supercooling section is blocked, the cold source function of low-temperature air outlet of the evaporator after dehumidification is fully developed, the temperature of the condensate at the tail end of the condenser is greatly reduced, namely deep supercooling of the condensate at the tail end of the condenser is implemented, the vaporization ratio of the refrigerant in the throttling process is greatly reduced, namely the dryness of the refrigerant at the inlet of the evaporator at the outlet of the throttling valve is greatly reduced, the refrigerating capacity of the evaporator is greatly improved, and the dehumidification energy efficiency ratio is greatly improved.
(2) Size reduction of dehumidifier
According to the invention, through arranging the evaporator-condenser combination, the air flow at the inlet of the dehumidifier passes through the evaporator to cool and dehumidify, then passes through the tail end of the condenser and then passes through the middle section of the condenser to implement twice reheating, so that the path of the air flow at the inlet of the dehumidifier is extended, the size of the evaporator-condenser module is reduced, and the size of an air duct is reduced.
Of course, it is not necessary for any product in which the invention is practiced to achieve all of the above-described advantages at the same time.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts. In the drawings:
fig. 1 is a schematic structural diagram of a dehumidifier, which is filed by refrigeration equipment limited in Guangdong America in 2017, 12 and 22 months and has an application number of 201711417767.4 and an invention name of the dehumidifier;
FIG. 2 is a schematic diagram of a high efficiency dehumidifier named 201510117040.9 filed by Shanghai Bernoulli culvert thermal energy science and technology Limited on 17.03.2015 to the national intellectual Property office;
fig. 3 is a schematic structural diagram of a dehumidifier named as the dehumidifier, which is filed by the electric company nai bao in foshan city in 2017, 09 and 30, and has an application number of 201710940612.2 by the national intellectual property office;
FIG. 4 is a schematic diagram of mathematical logic deduction on a pressure-enthalpy diagram for increasing the supercooling degree of condensate of a dehumidifier condenser to enlarge the refrigeration capacity and the dehumidification capacity of an evaporator;
FIG. 5 is a schematic diagram of the operation of a dehumidifier in which each section of the condenser employs finned tube heat exchangers of the same diameter;
fig. 6 is a schematic structural diagram of a two-unit module of a subcooling section of a fin-tube heat exchanger with a small diameter according to preferred embodiment 1 of the present invention;
FIG. 7 is an operation diagram of a two-unit module of a subcooling section using a small-diameter finned tube heat exchanger according to preferred embodiment 1 of the present invention;
fig. 8 is a schematic structural diagram of a two-unit module of a subcooling section of a fin-tube heat exchanger with a small diameter according to preferred embodiment 2 of the present invention;
fig. 9 is an operation diagram of a two-unit module of a subcooling section using a fin-tube heat exchanger with a small diameter according to preferred embodiment 2 of the present invention.
Detailed Description
The present invention will be described in detail with reference to specific examples. The following examples will assist those skilled in the art in further understanding the invention, but are not intended to limit the invention in any way. It should be noted that it would be obvious to those skilled in the art that various changes and modifications can be made without departing from the spirit of the invention. All falling within the scope of the present invention.
Example 1
The dehumidification energy efficiency, namely the quality of water vapor filtered from air under specified working conditions (such as 60% standard working conditions at 27 ℃ in China and 60% standard working conditions at 80 DEG F in the United states) by using 1kwh of electric energy consumed by the dehumidifier is a core technical index of the dehumidifier; the dehumidification energy efficiency is improved, and the method is a permanent technical innovation subject in the dehumidifier industry.
The dehumidification energy efficiency is improved, the energy efficiency of a compressor (refrigerant side-pushing power) and a fan (air side-pushing power) which are main parts of the dehumidifier is greatly improved, the spatial structure relation of an evaporator condenser is optimized, and 2 technical goals of reducing condensation pressure by using large air volume of the condenser and realizing deep supercooling of condensate by using low-temperature air outlet of the evaporator are realized.
Through the common efforts of the dehumidifier industry and enterprises, the high-energy-efficiency compressor, the high-energy-efficiency fan and the technical standard rod for expanding the air quantity of the condenser and reducing the condensing pressure by recombining the space structure relationship of the evaporator condenser are repeatedly lifted and realized at a high level; however, the dehumidifier enterprise has unclear understanding and inaccurate judgment on the technical meaning of improving the supercooling degree of the condensate at the tail end of the condenser, so that the aim of reducing the temperature of the condensate at the tail end of the condenser by using low-temperature outlet air of the evaporator to realize deep supercooling of the refrigerant is far from being realized.
Referring to fig. 6 to 9, the present invention provides an ultra-high energy efficiency dehumidifier for cutting off thermal bridge connection between a supercooling section and a condensing section fin, including:
the two-unit combined module 1 comprises a condenser 11 and an evaporator 12, wherein the condenser 11 comprises an overheating heat release section 111, a condensation section 112 and a supercooling section 113, and the overheating heat release section 111, the condensation section 112, the supercooling section 113 and the evaporator 12 are all fin-tube heat exchangers; the evaporator 12, the supercooling section 113 and the condensing section 112 are sequentially arranged side by side, and refrigerant pipelines of the superheating heat release section 111, the condensing section 112 and the supercooling section 113 are sequentially connected in series; the inner diameter of the refrigerant pipe of the supercooling section 113 is smaller than that of the refrigerant pipe of the condensation section 112; the output end of the supercooling section 113 of the condenser 11 is communicated with the input end of the evaporator 12 through a throttling device 13;
the fan 3 is positioned at one side close to the supercooling section 113; under the suction action of the fan 3, the main air flow at the inlet of the dehumidifier firstly passes through the evaporator 12 for cooling and dehumidifying, then sequentially passes through the supercooling section 113 and the condensation section 112 of the condenser 11 for reheating twice, and finally is discharged by the fan 3;
the input end of the two-unit combination module 1 is communicated with the output end of the compressor 2, and the output end of the two-unit combination module 1 is communicated with the input end of the compressor 2 to form a refrigerant circulation channel; the input end of the two combination modules 1 is the input end of the overheating heat release section 111 of the condenser 11, and the output end of the two combination modules 1 is the output end of the evaporator 12;
the two combined modules 1, the fan 3 and the compressor 2 are all arranged in the shell 4; the shell 4 is provided with an inlet and an outlet, the air inlet of the evaporator 12 faces the inlet, the air outlet of the fan 3 faces the outlet, and under the suction action of the fan 3, the main airflow at the inlet of the dehumidifier firstly passes through the evaporator 12 for cooling and dehumidifying, then sequentially passes through the supercooling section 113 and the condensation section 112 of the condenser 11 for reheating twice, and finally is discharged through the outlet of the dehumidifier.
The invention provides an ultra-high energy efficiency dehumidifier for cutting off connection between a supercooling section and a fin thermal bridge of a condensing section, which is based on judgment that the improvement of the supercooling degree of a refrigerant liquid at the tail end of a condenser is that the evaporation proportion of the refrigerant liquid in a throttling valve is reduced, so that the evaporation proportion of the refrigerant liquid in an evaporator is improved, and the dehumidification capacity of the refrigerant is improved.
The refrigerating capacity of the dehumidifier evaporator is the product of the refrigerant circulation capacity and the enthalpy difference of the refrigerant at the inlet and the outlet of the evaporator. The enthalpy difference of the refrigerant at the inlet and the outlet of the evaporator is negatively related to the dryness of the refrigerant entering the inlet of the evaporator from the outlet of the throttle valve; the dryness of the refrigerant at the inlet of the evaporator is the ratio of the gaseous refrigerant to the gas-liquid two-phase flow of the refrigerant, the dryness is lower, namely the dryness is closer to 0, namely the gaseous ratio is low (close to 0) and the liquid ratio is high (close to 1.0), the 'integrity' of the refrigerant entering the evaporator is high, the enthalpy difference of the refrigerant at the inlet and the outlet of the evaporator is increased, the refrigerating capacity of the evaporator is increased, and the dehumidifying capacity is increased; on the contrary, the dryness of the refrigerant at the inlet of the evaporator is increased, the 'integrity' of the refrigerant entering the evaporator is reduced, the enthalpy difference of the refrigerant at the inlet and the outlet of the evaporator is reduced, the refrigerating capacity is reduced, and the dehumidifying capacity is reduced.
The dryness of the refrigerant at the outlet of the throttle valve and the inlet of the evaporator is determined by the supercooling degree of the refrigerant at the tail end of the condenser (namely the inlet of the throttle valve): in the throttling and pressure reducing process of the refrigerant in the throttling valve, in order to reduce the temperature of high-pressure and high-temperature refrigerant at the outlet of the condenser and the inlet of the throttling valve to the saturation temperature corresponding to the low-pressure state at the outlet of the throttling valve and the inlet of the evaporator, in the throttling operation of the throttling valve, one part of liquid refrigerant is vaporized and absorbs heat, and the other part of liquid refrigerant is cooled, so that the refrigerant injected into the inlet of the evaporator is not the liquid refrigerant with the dryness of 0 but a gas-liquid two-phase flow with the dryness of x, wherein the dryness of x can be 0.2 (liquid ratio of 0.8), 0.3 (liquid ratio of 0.7), or 0.4 (liquid ratio of 0.6) or even 0.5 (liquid ratio of 0.5).
Therefore, the refrigerating fluid at the tail end of the condenser has sufficient heat release, high supercooling degree and low temperature, so that the temperature difference of the cooling fluid to the evaporation temperature is small and the heat release amount is small in the throttling operation of the throttling valve, the proportion of the refrigerating fluid vaporized and absorbed in the throttling valve is relatively low, the dryness of the refrigerating fluid at the outlet of the throttling valve and the inlet of the evaporator is relatively low, x is as low as 0.2 or even below 0.2, and the refrigerating capacity of the evaporator is relatively large; on the contrary, the refrigerating fluid at the tail end of the condenser has insufficient heat release, low supercooling degree and high temperature, so that the temperature difference of the refrigerating fluid cooled to the evaporation temperature is large and the heat release amount is large in the throttling operation of the throttling valve, the proportion of the refrigerating fluid vaporized and absorbed in the throttling valve is relatively high, the dryness of the refrigerating fluid at the outlet of the throttling valve and the inlet of the evaporator is relatively high, x is 0.3 or even more than 0.4, and the refrigerating capacity of the evaporator is relatively small.
Therefore, the ' improvement of the supercooling degree of the refrigerating fluid at the tail end of the condenser ' is to reduce the vaporization proportion of the refrigerating fluid in the throttling valve, so that the evaporation proportion of the refrigerating fluid in the evaporator is improved, and the dehumidification capacity of the refrigerating capacity is improved '.
As shown in figure 4, the condensate at the tail end of the condenser of the dehumidifier is greatly cooled to implement deep supercooling, and the state of the refrigerant liquid before the throttle valve on the pressure-enthalpy diagram is moved from a point 5 to the left to a point 5 ， The "quality" of the two-phase gas-liquid flow of refrigerant injected into the evaporator after the corresponding "throttling" of the refrigerant liquid decreases from 0.32 (liquid phase 0.68) at point 6 to point 6 ， 0.08 (0.92 liquid phase), the refrigerant liquid phase ratio is increased by 0.92-0.68=0.24 (24%), based on 0.68 of the liquid phase ratio in the refrigerant gas-liquid two-phase flow at the evaporator inlet point 6 before the improvement, the evaporator inlet point 6 after the condenser end condensate deep subcooling improvement is performed ， The liquid phase ratio of the evaporator is improved by 0.24/0.68=35.3%, namely, the refrigerating capacity of the evaporator is improved by 35.3%; in addition, in the dehumidification process, the dehumidifier cools the sucked unsaturated air into saturated air with dew point temperature, and absorbs the refrigeration quantity consumed by sensible heat of the air from the unsaturated state to the temperature above the dew point temperature of the saturated air, so that the basic refrigeration quantity is equal to the fixed cost in enterprise cost, and is the cost before the effective output of the enterprise occurs, and the basic refrigeration quantity does not generate the dehumidification effect, so that the dehumidification quantity increment caused by 35.3% of the evaporator refrigeration quantity increased by adopting the deep supercooling technology in the embodiment exceeds 35.3% and reaches about 40%, and the theoretical limit of the dehumidification energy efficiency under the standard working condition of the common dehumidifier is directly approached to 4.0L/kwh.
In summary, based on the principle of "increasing the degree of supercooling of the refrigerant at the end of the condenser, that is, reducing the vaporization ratio of the refrigerant in the throttle valve, thereby increasing the evaporation ratio of the refrigerant in the evaporator and increasing the cooling capacity and dehumidification", referring to fig. 5 to 9, the combined module of the evaporator 12 and the condenser 11 provided in this embodiment splits the condenser 11 into three sections, that is, a high-temperature sensible heat release section (the front end of the condenser 11, abbreviated as a superheating heat release section 111), a latent heat release section (the middle section of the condenser 11, abbreviated as a condensing section 112), and a supercooling superheating heat release section 111 (the end of the condenser 11, abbreviated as a supercooling section 113) which respectively correspond to the high-temperature and high-pressure refrigerant gas discharged from the compressor 2, and sequentially connects in series, and the end of the condenser 11, that is, the supercooling section 113, is disposed between the evaporator 12 and the main condensing section 112 of the condenser 11, thereby increasing the cooling effect of the refrigerant condensate from the low-temperature air discharged from the evaporator 12, and increasing the degree of supercooling of the refrigerant at the end of the condenser 11, thereby increasing the cooling capacity and the dehumidification capacity of the evaporator 12.
However, as shown in fig. 5, if the inner diameters of the refrigerant pipes of the superheating heat-releasing section 111, the condensing section 112, and the supercooling section 113 are the same, the liquefaction phase change of the refrigerant gas is already completed in the middle section (condensing section 112) of the condenser 11, and compared with the condensation phase change heat exchange in the middle section of the condenser 11 having the characteristic of high convective heat exchange coefficient, the fully liquid refrigerant condensate flows in the heat exchanger pipe at the end (supercooling section 113) of the condenser 11, and therefore, the flow rate is low, the reynolds number is low, the convective heat exchange coefficient is low, the heat exchange strength is seriously low, and the improvement of the supercooling degree of the condensate is restricted.
Determining the Reynolds number Re of the refrigerant and the convection heat transfer coefficient alpha because of the flow velocity of the refrigerant;
at the end of the condenser 11 line, the reynolds number of the condensate: re = d × u × ρ/μ (where d — the inner pipe passage, u — the refrigerant flow rate, ρ — the refrigerant density, μ — the refrigerant viscosity).
And the Nu = alpha x d/lambda =0.023Re 0.8 ×Pr n ( Wherein, alpha-convection heat transfer coefficient, lambda-refrigerant heat conduction coefficient, re-Reynolds number, pr-Plantet number; index n, heat release 0.3 and heat absorption 0.4 )
The heat transfer coefficient of the convection of the condensate at the tail end of the condenser 11 and the inner wall of the pipeline can be deduced
α＝A×u 0.8 /d 0.2 (where A is a constant, u- -refrigerant flow rate, d- -inner diameter of tube)
At the end of the condenser 11, the refrigerant gas condensation phase change is finished, the gas-liquid two-phase flow is converted into liquid single-phase flow, the volume flow V of the refrigerant liquid is stable, the flow velocity u is stable, andand u is inversely proportional to the 2 nd power of the inner diameter d, thus from α = a × u 0.8 /d 0.2 At the end of the condenser 11 (i.e. the supercooling section 113):
α∝1/d 1.8
taking a dehumidifier with 1.5HP using R134a refrigerant and a 7mm fin-and-tube heat exchanger as an example, the volumetric flow rate of refrigerant gas at the inlet of the condenser 11 (the inlet of the superheating heat-releasing section 111) is about 0.82m 3 H, a flow rate of about 4.6m/s; at the end of the condenser 11, the condensate has a density of 1052.9kg/m 3 The flow velocity of the refrigerant is reduced to 0.38m/s, and the convective heat transfer coefficient of the condensate inside the pipeline at the tail end of the condenser 11 and the pipeline wall is alpha = A × u 0.8 /d 0.2 Measured and calculated that the alpha value is 10 2 The grade is about 600W/(. Square-meter.times.C.), and only 1/5-1/10 of the coefficient of heat exchange of evaporation and condensation phase change is available.
From the above, increasing the flow rate U of the condensate is the most effective way to increase the convective heat transfer coefficient α between the condensate at the end of the condenser 11 and the inner wall of the pipeline.
Therefore, referring to fig. 6 and 7, in this embodiment, the inner diameter of the refrigerant pipe 131 of the supercooling section 113 is preferably smaller than that of the refrigerant pipe of the condensation section 112, and the inner diameters of the refrigerant pipes of the superheating heat releasing section 111, the condensation section 112 and the evaporator 12 are the same. Taking the thin-diameter finned tube heat exchanger with the diameter of 5mm and below as an example of the supercooling section 113 of the condenser 11, compared with the method that the finned tube heat exchanger with the diameter of 7mm is adopted in the supercooling section 113, the flow speed of the refrigerant liquid in the supercooling section 113 is greatly improved by more than 1 time, and the convection heat exchange coefficient alpha (which is greater than or equal to 1/d) of the refrigerant liquid at the inner side of the tube 1.8 ) The refrigerant liquid supercooling effect at the tail end of the condenser 11 and the dehumidification energy efficiency ratio of the dehumidifier are further improved by 83.2 percent correspondingly and greatly.
In the present embodiment, the evaporator 12 is embedded in the condenser 11. Specifically, the superheating heat release section 111 is located above the evaporator 12, the supercooling section 113 and the condensing section 112 which are arranged side by side.
In this embodiment, the superheating heat-releasing section 111, the condensing section 112, the supercooling section 113 and the refrigerant pipeline of the evaporator 12 are connected in series in sequence, and the refrigerant pipeline output port of the supercooling section 113 is communicated with the refrigerant pipeline input port of the evaporator 12 through the throttling device 13. The throttling device 13 may be a throttling valve, an electronic expansion valve, a capillary vessel, or the like. In the present embodiment, the evaporator 2 has only one refrigerant line.
The tail end of the condenser 11 in the embodiment adopts the thin-diameter finned tube heat exchanger, so that the flow speed and Reynolds number of the refrigerant liquid at the tail end of the condenser 11 and the convection heat transfer coefficient of the refrigerant liquid at the inner side of the tube are improved, and the heat release effect of the refrigerant condensate on low-temperature air outlet of the evaporator 12 is improved.
The invention is based on the technical combination that the supercooling section 113 adopts a thin-diameter fin tube type heat exchanger, the thin-diameter fin tube type heat exchanger is adopted at the tail end of the condenser 11 (the supercooling section 113 of the refrigerant liquid), simultaneously, the fin heat bridge connection between different temperature areas of the condenser 11 is cut off to block the heat transfer of the high-temperature area to the supercooling section 113, the deep supercooling of the condensate liquid of the condenser 11 is implemented at a higher level, the vaporization proportion of the refrigerant liquid in the throttling valve is reduced, and the refrigerating capacity of the evaporator 12 is improved to achieve the dehumidification energy efficiency approaching the theoretical limit.
The two-unit combined module of the condenser 11 with the supercooling section 113 adopting the thin-diameter finned tube heat exchanger has the advantages that aiming at the problems of low flow velocity and reynolds number of condensate, low heat convection coefficient and serious low heat exchange strength of the condensate existing in a heat exchanger pipeline at the tail end of the condenser, the supercooling section 113 of the condenser 11 adopts the thin-diameter finned tube heat exchanger with the diameter of 5mm or less, so that the flow velocity and the reynolds number of the refrigerant at the tail end of the condenser 11 and the heat convection coefficient of the refrigerant at the inner side of the tube are improved, and the cooling effect of the low-temperature air outlet of the evaporator 12 on the condensate of the refrigerant is improved; the technical combination of the thin-diameter finned tube heat exchangers is adopted on the basis of the supercooling section 113, the thin-diameter finned tube heat exchangers are adopted at the tail ends of the condensers 11, fin heat bridge connection among different temperature areas of the condensers 11 is cut off to block heat transfer of a high-temperature area to the supercooling section 113, deep supercooling of condensate of the condensers is implemented at a higher level, the evaporation ratio of refrigerant in a throttling valve is reduced, and the refrigerating capacity of the evaporators 12 is improved to achieve dehumidifier dehumidification energy efficiency of 4.0L/kwh approaching to the theoretical limit under the standard working condition; meanwhile, the small-diameter fin tube type heat exchanger adopted at the tail end of the condenser 11 in the embodiment also has the advantages of high mechanical strength and good heat exchange uniformity.
Example 2
This example is a further improvement on example 1. In this embodiment, referring to fig. 8 and fig. 9, the refrigerant pipeline of the evaporator 12 includes at least two refrigerant sub-pipelines 1121 connected in parallel, and the refrigerant pipeline output ports of the subcooling section 113 of the condenser 11 are respectively communicated with the input ports of the refrigerant sub-pipelines 1121 through throttling devices 13. The number of refrigerant sub-circuits 1121 is not limited in this embodiment, and the evaporator 12 is shown to include three refrigerant sub-circuits 1121 in parallel. In the embodiment, based on the judgment that the volume flow of the refrigerant gas at the tail end of the evaporator reaches more than 3 times of the front end of the condenser, the flowing speed and the on-way resistance of the refrigerant in the pipeline of the evaporator are greatly increased relative to the condenser, the suction pressure of the compressor is seriously reduced, and the circulation quantity and the refrigerating capacity of the refrigerant are seriously reduced, 3-way parallel connection is adopted to reduce the pressure difference of the inlet and the outlet of the evaporator 12, the suction pressure of the compressor is improved, and the circulation quantity, the refrigerating capacity, the dehumidifying capacity and the dehumidifying efficiency of the refrigerant are improved on the basis that a phi 5 fine-diameter finned tube heat exchanger is adopted at the supercooling section 113 of the condenser 11.
The foregoing description of specific embodiments of the present invention has been presented. It is to be understood that the present invention is not limited to the specific embodiments described above, and that various changes or modifications may be made by one skilled in the art within the scope of the appended claims without departing from the spirit of the invention. The embodiments and features of the embodiments of the present application may be combined with each other arbitrarily without conflict.
Claims (10)
1. The utility model provides a super high energy efficiency dehumidifier of cutting off super-cooling section and condensation section fin heat bridge relation which characterized in that includes:
the two-unit combined module comprises a condenser and an evaporator, the condenser comprises an overheating heat release section, a condensation section and a supercooling section, and the overheating heat release section, the condensation section, the supercooling section and the evaporator are all fin tube type heat exchangers; the evaporator, the supercooling section and the condensing section are sequentially arranged in parallel, and refrigerant pipelines of the overheating heat release section, the condensing section and the supercooling section are sequentially connected in series; the inner diameter of the refrigerant pipeline of the supercooling section is smaller than that of the refrigerant pipeline of the condensation section; the output end of the supercooling section of the condenser is communicated with the input end of the evaporator through a throttling device;
the main air flow at the inlet of the dehumidifier firstly passes through the evaporator to reduce the temperature and dehumidify under the suction action of the fan, then sequentially passes through the supercooling section and the condensing section of the condenser to implement twice reheating, and finally is discharged by the fan;
the input end of the two-unit combination module is communicated with the output end of the compressor, and the output end of the two-unit combination module is communicated with the input end of the compressor to form a refrigerant circulation channel; the input end of the two combined modules is the input end of the overheat heat release section of the condenser, and the output end of the two combined modules is the output end of the evaporator.
2. The ultra-high energy efficiency dehumidifier for cutting off the thermal bridge connection between the supercooling section and the fins of the condensation section according to claim 1, wherein the evaporator is embedded in the condenser.
3. The dehumidifier of claim 2, wherein the overheating heat release section is located above the evaporator, the supercooling section and the condensing section which are arranged side by side.
4. The ultra-high energy efficiency dehumidifier for cutting off the thermal bridge connection between the supercooling section and the fin of the condensing section in claim 1, wherein the refrigerant pipelines of the superheating heat release section, the condensing section and the evaporator have the same inner diameter.
5. The dehumidifier of claim 4, wherein the inside diameter of the refrigerant pipeline of the condensation section is 9mm, and the inside diameter of the refrigerant pipeline of the supercooling section is not more than 7mm.
6. The dehumidifier of claim 4, wherein the inside diameter of the refrigerant pipeline of the condensation section is 7mm, and the inside diameter of the refrigerant pipeline of the supercooling section is not more than 5mm.
7. The dehumidifier of claim 1, wherein the superheating heat release section, the condensation section, the supercooling section and the refrigerant pipeline of the evaporator are connected in series in sequence, and the refrigerant pipeline output port of the supercooling section is communicated with the refrigerant pipeline input port of the evaporator through the throttling device.
8. The dehumidifier of claim 1, wherein the refrigerant pipeline of the evaporator comprises at least two refrigerant sub-pipelines connected in parallel, and the refrigerant pipeline outlet of the supercooling section is respectively communicated with the inlets of the refrigerant sub-pipelines through the throttling device.
9. The ultra-high energy efficiency dehumidifier for cutting off the thermal bridge connection between the supercooling section and the fins of the condensing section according to claim 1, wherein the fan is positioned at one side close to the condenser.
10. The dehumidifier with ultra-high energy efficiency and capable of cutting off the thermal bridge connection between the supercooling section and the fins of the condensation section according to claim 1, further comprising a shell, wherein the two combined modules, the fan and the compressor are arranged in the shell;
the shell is provided with the inlet and the outlet, the air inlet of the evaporator faces the inlet, and the air outlet of the fan faces the outlet.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210676911.0A CN115218299B (en) | 2022-06-16 | 2022-06-16 | Super high energy efficiency dehumidifier for cutting off heat bridge connection between super cooling section and condensing section fins |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210676911.0A CN115218299B (en) | 2022-06-16 | 2022-06-16 | Super high energy efficiency dehumidifier for cutting off heat bridge connection between super cooling section and condensing section fins |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN115218299A true CN115218299A (en) | 2022-10-21 |
| CN115218299B CN115218299B (en) | 2024-05-28 |
Family
ID=83608783
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210676911.0A Active CN115218299B (en) | 2022-06-16 | 2022-06-16 | Super high energy efficiency dehumidifier for cutting off heat bridge connection between super cooling section and condensing section fins |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115218299B (en) |
Citations (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000111094A (en) * | 1998-10-05 | 2000-04-18 | Ebara Corp | Dehumidifier/air conditioner and dehumidifying/air conditioning system |
| JP2002340437A (en) * | 1993-06-01 | 2002-11-27 | Hitachi Ltd | Air conditioner |
| CN2704777Y (en) * | 2004-07-04 | 2005-06-15 | 王永明 | Integrated effective cooling driers |
| US20090241573A1 (en) * | 2008-03-27 | 2009-10-01 | Denso Corporation | Refrigerant cycle device |
| CN101846362A (en) * | 2009-03-26 | 2010-09-29 | 乐金电子(天津)电器有限公司 | Improved structure of dehumidifier |
| CN203011009U (en) * | 2012-11-22 | 2013-06-19 | 郑州轻工业学院 | Novel heat exchanger structure for air conditioner |
| CN104019574A (en) * | 2014-05-16 | 2014-09-03 | 上海伯涵热能科技有限公司 | Low-condensing-pressure deep supercooling efficient dehumidifier |
| CN104075495A (en) * | 2013-03-26 | 2014-10-01 | 珠海格力电器股份有限公司 | Air conditioner and finned heat exchanger |
| CN104532524A (en) * | 2014-11-28 | 2015-04-22 | 上海伯涵热能科技有限公司 | Laterally-arranged heat pump clothes drying cabinet of deep dehumidification device |
| CN104764116A (en) * | 2015-03-17 | 2015-07-08 | 上海伯涵热能科技有限公司 | High-efficient dehumidifier |
| CN106369715A (en) * | 2016-09-20 | 2017-02-01 | 清华大学 | Composite internally-cooled liquid desiccant air conditioning unit driven by heat pump |
| CN106705504A (en) * | 2017-01-04 | 2017-05-24 | 合肥华凌股份有限公司 | Condenser and refrigeration device |
| CN108800668A (en) * | 2018-08-13 | 2018-11-13 | 沈珂 | A kind of the cooling heat exchange device and its control method of energy saving dehumidifying |
| CN111059802A (en) * | 2019-12-16 | 2020-04-24 | 珠海格力电器股份有限公司 | Condensing equipment and air conditioning system who has it |
| CN112268385A (en) * | 2020-10-30 | 2021-01-26 | 上海伯涵热能科技有限公司 | Dehumidifying, cooling, heating and drying air conditioner capable of recovering heat |
| US20210102738A1 (en) * | 2019-10-07 | 2021-04-08 | Johnson Controls Technology Company | Modulating reheat operation of hvac system |
| CN114111313A (en) * | 2021-11-25 | 2022-03-01 | 同济大学 | Dehumidification drying heat pump system fusing compressor driving type quasi loop heat pipe |
| CN218001684U (en) * | 2022-06-16 | 2022-12-09 | 上海伯涵热能科技有限公司 | Condenser adopting micro-channel heat exchanger in supercooling section and two-unit combined module |
| CN218001685U (en) * | 2022-06-16 | 2022-12-09 | 上海伯涵热能科技有限公司 | Heat exchanger combined module adopting thin-diameter fin tube type heat exchanger in supercooling heat release section |
-
2022
- 2022-06-16 CN CN202210676911.0A patent/CN115218299B/en active Active
Patent Citations (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002340437A (en) * | 1993-06-01 | 2002-11-27 | Hitachi Ltd | Air conditioner |
| JP2000111094A (en) * | 1998-10-05 | 2000-04-18 | Ebara Corp | Dehumidifier/air conditioner and dehumidifying/air conditioning system |
| CN2704777Y (en) * | 2004-07-04 | 2005-06-15 | 王永明 | Integrated effective cooling driers |
| US20090241573A1 (en) * | 2008-03-27 | 2009-10-01 | Denso Corporation | Refrigerant cycle device |
| CN101846362A (en) * | 2009-03-26 | 2010-09-29 | 乐金电子(天津)电器有限公司 | Improved structure of dehumidifier |
| CN203011009U (en) * | 2012-11-22 | 2013-06-19 | 郑州轻工业学院 | Novel heat exchanger structure for air conditioner |
| CN104075495A (en) * | 2013-03-26 | 2014-10-01 | 珠海格力电器股份有限公司 | Air conditioner and finned heat exchanger |
| CN104019574A (en) * | 2014-05-16 | 2014-09-03 | 上海伯涵热能科技有限公司 | Low-condensing-pressure deep supercooling efficient dehumidifier |
| CN104532524A (en) * | 2014-11-28 | 2015-04-22 | 上海伯涵热能科技有限公司 | Laterally-arranged heat pump clothes drying cabinet of deep dehumidification device |
| CN104764116A (en) * | 2015-03-17 | 2015-07-08 | 上海伯涵热能科技有限公司 | High-efficient dehumidifier |
| CN106369715A (en) * | 2016-09-20 | 2017-02-01 | 清华大学 | Composite internally-cooled liquid desiccant air conditioning unit driven by heat pump |
| CN106705504A (en) * | 2017-01-04 | 2017-05-24 | 合肥华凌股份有限公司 | Condenser and refrigeration device |
| CN108800668A (en) * | 2018-08-13 | 2018-11-13 | 沈珂 | A kind of the cooling heat exchange device and its control method of energy saving dehumidifying |
| US20210102738A1 (en) * | 2019-10-07 | 2021-04-08 | Johnson Controls Technology Company | Modulating reheat operation of hvac system |
| CN111059802A (en) * | 2019-12-16 | 2020-04-24 | 珠海格力电器股份有限公司 | Condensing equipment and air conditioning system who has it |
| CN112268385A (en) * | 2020-10-30 | 2021-01-26 | 上海伯涵热能科技有限公司 | Dehumidifying, cooling, heating and drying air conditioner capable of recovering heat |
| CN114111313A (en) * | 2021-11-25 | 2022-03-01 | 同济大学 | Dehumidification drying heat pump system fusing compressor driving type quasi loop heat pipe |
| CN218001684U (en) * | 2022-06-16 | 2022-12-09 | 上海伯涵热能科技有限公司 | Condenser adopting micro-channel heat exchanger in supercooling section and two-unit combined module |
| CN218001685U (en) * | 2022-06-16 | 2022-12-09 | 上海伯涵热能科技有限公司 | Heat exchanger combined module adopting thin-diameter fin tube type heat exchanger in supercooling heat release section |
Non-Patent Citations (1)
| Title |
|---|
| 姜盈霓;虎小红;: "流程布置对翅片管换热器换热性能影响的研究现状与展望", 制冷与空调, no. 03, 28 June 2007 (2007-06-28), pages 20 - 26 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN115218299B (en) | 2024-05-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104764116B (en) | A kind of high-efficiency dehumidifier | |
| Zhang et al. | A frost-free dedicated outdoor air system with exhaust air heat recovery | |
| CN104019574A (en) | Low-condensing-pressure deep supercooling efficient dehumidifier | |
| Zhang et al. | Optimization analysis of a hybrid fresh air handling system based on evaporative cooling and condensation dehumidification | |
| CN204786909U (en) | High -efficient dehumidifier | |
| CN103471296B (en) | Operation of air conditioning systems | |
| CN205641690U (en) | Double heating type combined type air conditioner system | |
| Kwak et al. | Effect of part load operating conditions of an air conditioner on the number of refrigerant paths and heat transfer performance of a condenser | |
| CN102692101A (en) | Heat exchanger and air conditioner equipment | |
| CN218001685U (en) | Heat exchanger combined module adopting thin-diameter fin tube type heat exchanger in supercooling heat release section | |
| CN206803544U (en) | Refrigeration experiment double-machine two-stage compression refrigerating system | |
| Enteria et al. | Review of the advances and applications of variable refrigerant flow heating, ventilating, and air-conditioning systems for improving indoor thermal comfort and air quality | |
| CN203928478U (en) | A kind of low condensing pressure degree of depth is crossed cold high-efficiency dehumidifier | |
| JPH06213518A (en) | Heat pump type air conditioner for mixed refrigerant | |
| CN1156662C (en) | Heat pump system | |
| CN204630441U (en) | A kind of separated high-efficiency heat pipe heat exchanger | |
| CN218001684U (en) | Condenser adopting micro-channel heat exchanger in supercooling section and two-unit combined module | |
| CN112268321B (en) | Mixed working medium refrigerating system and dehumidifier | |
| CN206113408U (en) | Can change air source heat pump unit of frost | |
| CN115218299B (en) | Super high energy efficiency dehumidifier for cutting off heat bridge connection between super cooling section and condensing section fins | |
| Hai et al. | Design and research of the digital VRV multi-connected units with three pipes type heat recovery system | |
| CN202660821U (en) | Concurrent flow type condenser and air conditioner using same | |
| CN205119917U (en) | Improve condensate coefficient of convective heat transfer's component and refrigerating system , warm air conditioner ware that cools | |
| CN108613383A (en) | A kind of sludge drying heat pump system | |
| Cao et al. | Analysis and experiment of stepped pressure cycle performance conditional on evaporator superheat |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| TA01 | Transfer of patent application right | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20230406 Address after: Room R21-A124, Room 403, No. 1, Mingzhu 1st Street, Hengli Town, Nansha District, Guangzhou City, Guangdong Province, 511466 Applicant after: Guangzhou Wan'ermei Engineering Technology Co.,Ltd. Address before: Room 203, building 1, No. 23 and 33, Lane 466, Yindu Road, Minhang District, Shanghai Applicant before: SHANGHAI BOHAN THERMAL ENERGY TECHNOLOGY Co.,Ltd. |
|
| GR01 | Patent grant | ||
| GR01 | Patent grant |