Super heavy load super high energy efficiency dehumidifier

Abstract

This invention belongs to the field of new energy technology and discloses an ultra-high efficiency dehumidifier with heavy load capacity, including a shell, a dehumidifier assembly, a compressor, and an exhaust chamber. The negative pressure chamber is composed of the dehumidifier assembly, part of the shell, and a back plate. The back plate is provided with several air outlets of the negative pressure chamber, and each air outlet is equipped with a vertically arranged fan. The dehumidifier assembly is located on the air inlet side of the shell and serves as the air inlet of the negative pressure chamber. The air outlets on the back plate correspond to the air inlets of the vertically arranged fans. The air outlets are connected to the exhaust chamber. The exhaust outlet of the exhaust chamber is located on the side plate, top plate, or back plate of the shell. The shell contains two sets of dehumidifier assemblies and their negative pressure chambers. The shell also contains a compressor chamber for housing a refrigerant circuit assembly including a compressor, a gas-liquid separator, and an electrical box.

Description

Technical Field

[0001] This invention belongs to the field of new energy technology, and in particular relates to an ultra-high energy efficiency dehumidifier with heavy load capacity. Background Technology

[0002] A typical dehumidifier is a single-cooling air conditioner that uses both an evaporator and a condenser (two units) to share a single airflow path. It dehumidifies by absorbing heat from the evaporator and cooling the air drawn in through the gaps between the fins to below the dew point temperature, causing moisture to condense and fall off. As the simplest refrigeration product, dehumidifiers are characterized by their wide variety and large production volume. Along with air conditioners, refrigerators, and other refrigeration products, dehumidifiers have become an important pillar of modern manufacturing.

[0003] Existing technology discloses a dual-system dehumidifier with no blind-spot temperature regulation, comprising a housing and a dehumidifier body. The housing includes an upper housing and a lower housing, with the dehumidifier body located inside the lower housing. Air inlets are respectively provided on the side wall and top of the upper housing. A first mesh plate with a filter screen embedded in it is bolted to one end of each air inlet, and an air inlet pipe is fixed to the other end of the air inlet. This existing technology discloses a dual-system combined high-efficiency dehumidifier, aiming to solve the shortcomings of small air intake and poor condenser heat dissipation in dehumidifiers. The dehumidifier includes a main body and two dehumidification systems installed side-by-side inside the main body. Each dehumidification system includes a compressor, a main condenser, a secondary condenser, an evaporator, and a fan. The main body has a hollow compartment. Air inlets connected to the hollow compartment are located on the front, rear, left, and right sides of the main body. The secondary condensers of both dehumidification systems are installed at the rear air inlet. The evaporator and main condenser of one dehumidification system are installed between the front and left air inlets inside the hollow compartment, and the evaporator and main condenser of the other dehumidification system are installed between the front and right air inlets inside the hollow compartment. The air inlet of the fan is connected to the hollow compartment.

[0004] Current dehumidifier technology has not fully explored the role of low ambient temperature (27℃) in reducing condenser condensing pressure under standard operating conditions. In particular, it has not yet realized the important role of low-temperature evaporator outlet air (around 14℃) as an important cold source in reducing the condensate temperature at the end of the condenser, increasing the subcooling of the condensate, reducing the refrigerant vaporization ratio in the expansion valve, increasing the liquid phase ratio of refrigerant at the evaporator inlet, and increasing the dehumidification capacity. As a result, the dehumidification energy efficiency ratio of dehumidifiers has remained at around 2.0L / kwh for a long time.

[0005] Meanwhile, current dehumidifier technology continues the traditional single-duct structure, without focusing on optimizing the spatial relationship between the compressor, heat exchangers, and throttling valve. In particular, it does not focus on optimizing the spatial structural relationship between the heat exchangers and the inlet and outlet air ducts. This results in problems such as redundant structures and low energy density. The energy density has long remained at the level of 1L H2O / h dehumidification capacity occupying about 80L of main unit volume under standard operating conditions.

[0006] Significantly improving the dehumidification efficiency and load capacity of dehumidifiers, achieving a dehumidification efficiency of over 3.5L / kwh under standard operating conditions of 27℃ and 60%, and an energy density (load capacity) of less than 50L for each 1L H2O / h of dehumidification capacity, is the technological mission of the dehumidifier industry. Summary of the Invention

[0007] To address the aforementioned technical problems, this invention provides an ultra-high energy efficiency dehumidifier for heavy-duty applications.

[0008] To solve the above-mentioned technical problems, the technical solution of the present invention is as follows:

[0009] A heavy-duty, high-efficiency dehumidifier includes a housing, a dehumidifier assembly, a compressor, and an exhaust chamber. The negative pressure chamber is composed of the dehumidifier assembly, part of the housing, and a back panel. The back panel has several air outlets for the negative pressure chamber, each outlet equipped with a vertically arranged fan. The dehumidifier assembly is located on the air inlet side of the housing, serving as the air inlet for the negative pressure chamber. The air outlets on the back panel correspond to the air intakes of the vertically arranged fans. The air outlets connect to the exhaust chamber. The exhaust port of the exhaust chamber is located on the side panel, top panel, or back panel of the housing. The housing contains two sets of dehumidifier assemblies and their negative pressure chambers. The housing also contains a compressor chamber housing a refrigerant circuit assembly including a compressor, a gas-liquid separator, and an electrical box.

[0010] Furthermore, the back panel is provided with at least two air outlets; each air outlet is equipped with a fan, forming a fan wall; preferably, the fan is a centrifugal fan or an axial fan; more preferably, the centrifugal fan is a backward-curved external rotor centrifugal fan.

[0011] Preferably, the back panel is provided with 2, 4 or 6 air outlets; each air outlet is equipped with a fan, forming a fan wall.

[0012] Furthermore, the exhaust cavity is composed of a side plate of the housing, a bottom plate, a back plate of the negative pressure chamber, and an exhaust cavity back plate; preferably, the exhaust port of the exhaust cavity is a rectangular exhaust port.

[0013] Furthermore, the exhaust surface enclosed by the exhaust port is disposed on the top plate of the housing or the back plate of the exhaust cavity, and the air inlet surface is disposed on the front side of the housing or / and the long side adjacent to the front side.

[0014] Furthermore, a compressor chamber, including a compressor, a four-way valve, an expansion valve, and an electrical box, is provided on the outer side of the exhaust chamber back plate, or on the outer side of the negative pressure chamber, or below the exhaust chamber and / or the negative pressure chamber.

[0015] Furthermore, a water tank for collecting condensate is provided below the exhaust chamber and / or negative pressure chamber.

[0016] Furthermore, the compressor chamber is located between the two sets of dehumidifier assemblies, or on one side of the dehumidifier assemblies.

[0017] Furthermore, the exhaust port of the exhaust chamber is located on the top plate of the housing.

[0018] Furthermore, the dehumidifier assembly is composed of a horizontal cross-section V-shaped dual-unit module comprising at least two dual-unit combination modules; or it is composed of a dual-unit combination module and the horizontal cross-section V-shaped dual-unit combination module; or it is composed of one or two of the dual-unit combination module and the horizontal cross-section V-shaped dual-unit combination module, along with several partitions; the long side of the fins of the dual-unit combination module is arranged in the vertical direction or nearly vertical direction in the horizontal air duct; the horizontal cross-section of the dehumidifier assembly perpendicular to the long side of the fins is a sawtooth-shaped zigzag line.

[0019] The two-evapor combination module includes a condenser and an evaporator. The condenser includes a superheated heat release section, a condensing section, and a subcooling section. The superheated heat release section, the condensing section, the subcooling section, and the evaporator are all flat plate finned tube heat exchangers.

[0020] Furthermore, the horizontal cross-section of the dehumidifier assembly perpendicular to the long side of the fins is V-shaped or N-shaped, or it is composed of at least two V-shaped two-unit combination modules arranged continuously.

[0021] Preferably, the horizontal cross-section of the dehumidifier assembly perpendicular to the long side of the fins is W-shaped; preferably, the apex angle α of the V-shaped horizontal cross-section assembly module is 15° to 110°.

[0022] Preferably, the apex angle α of the horizontal cross-section V-shaped two-element combination module is 30° to 90°.

[0023] Preferably, the apex angle α of the horizontal cross-section V-shaped two-electrode combination module is 30° to 60°.

[0024] Furthermore, in the dehumidifier assembly, one side of the horizontal cross-section perpendicular to the long side of the fins is the air inlet surface of the heat exchanger, and the other side is the air outlet surface of the heat exchanger.

[0025] The incident surface of the airflow is the flat plate finned tube heat exchanger of each two-unit combination module. The angle between the airflow and the tip of each fin on each flat plate finned tube heat exchanger is an obtuse angle; the obtuse angle β is 97.5°~145°.

[0026] The incoming airflow impacts the tip of each fin in the flat-plate finned tube heat exchanger at an obtuse angle β, and is reflected by the fin tip plate into the fin gap and flows into the negative pressure chamber.

[0027] Furthermore, the airflow entering each fin gap d is equal to the airflow intercepted by the vertical distance δ between the tips of the two fins on the air inlet section of the flat plate finned tube heat exchanger.

[0028] δ=d·sinα / 2, where α is the apex angle of the horizontal cross-section V-shaped two-electrode combination module;

[0029] The vertical distance δ between the tips of the front and rear fins of the flat plate finned tube heat exchanger on the air inlet section is between 0.13d and 0.7d; preferably, the airflow velocity between the fins is 1 / 3 of the air inlet velocity, corresponding to the apex angle α of the horizontal cross-section V-shaped two-unit combined module being 39° and the incident obtuse angle β being 109.5°.

[0030] Furthermore, the evaporator, the subcooling section, and the condensing section are arranged adjacent to each other, with the evaporator embedded in the condenser; the superheated heat release section is located above the evaporator, the subcooling section, and / or the condensing section arranged side by side; the subcooling section is located between the condensing section and the evaporator. The refrigerant pipelines of the superheated heat release section, the condensing section, and the subcooling section are connected in series; the output end of the subcooling section of the condenser is connected to the input end of the evaporator through a throttling device.

[0031] Furthermore, the refrigerant lines of the superheated heat release section, condensing section, subcooling section, and evaporator are connected in series. The output end of the subcooling section of the condenser is connected to the input end of the evaporator through a throttling device. The refrigerant line output port of the subcooling section is connected to the refrigerant line input port of the evaporator through the throttling device. The refrigerant line of the evaporator includes at least two parallel refrigerant sub-lines. The refrigerant line output port of the subcooling section is connected to the input ports of several of the refrigerant sub-lines through the throttling device.

[0032] Furthermore, the two-unit combination module is equipped with two sets of condensers and two sets of evaporators; the two sets of condensers and two sets of evaporators in the two-unit combination module belong to two independent refrigeration and dehumidification systems.

[0033] Furthermore, the two condensers and two evaporators are mounted on the same finned assembly. On the fins, finned thermal bridges are provided between the heat exchange tube assemblies in the superheated heat release sections, which belong to each refrigeration and dehumidification system and are arranged adjacently, to form superheated heat release section combinations; finned thermal bridges are provided between the heat exchange tube assemblies in the condensing sections, which belong to each refrigeration and dehumidification system and are arranged adjacently, to form condensing section combinations; finned thermal bridges are provided between the heat exchange tube assemblies in the subcooling sections, which belong to each refrigeration and dehumidification system and are arranged adjacently, to form subcooling section combinations; and finned thermal bridges are provided between the heat exchange tube assemblies in the evaporators, which belong to each refrigeration and dehumidification system and are arranged adjacently, to form evaporator combinations.

[0034] On the fins, longitudinal and / or transverse gaps are provided between the superheated heat release section, condensing section, subcooling section and evaporator in the two-phase module to cut off the thermal bridges of the fins, and longitudinal and / or transverse fin ribs are provided to fix the relative spatial structural relationship of each area of ​​the fins.

[0035] Furthermore, the superheated heat release section, condensing section, subcooling section and evaporator are each composed of multiple refrigerant pipeline branches connected in parallel, and the heat exchange tube groups of each refrigerant pipeline branch are arranged side by side; preferably, the heat exchange tube groups are arranged alternately side by side.

[0036] Furthermore, the exhaust chamber and exhaust port are expanded into the compressor chamber, and the exhaust chamber and exhaust port have a T-shaped structure.

[0037] Compared with the prior art, the present invention has the following beneficial effects:

[0038] ① Explore the potential of the low-temperature outlet air of the evaporator and implement deep subcooling of condensate for efficient dehumidification.

[0039] This invention relates to an ultra-high load, ultra-high energy efficiency dehumidifier. The dehumidifier assembly consists of two sections, each consisting of an evaporator and a condenser. The condenser is divided into three sequentially connected segments corresponding to the high-temperature sensible heat release, latent heat release (condensation), and subcooling heat release of the high-temperature, high-pressure refrigerant gas discharged from the compressor. This design leverages the potential of the evaporator's low-temperature exhaust air after dehumidification, directing the cold exhaust air directly towards the condenser's end section, which performs the subcooling heat release function. Furthermore, it cuts off the fin thermal bridge between the condenser's end section (which performs subcooling heat release) and the middle section (which performs condensation heat release), blocking heat transfer from the high-temperature condensation zone to the subcooled zone at the condenser's end. This fully utilizes the "cold source" effect of the low-temperature exhaust air after dehumidification, significantly increasing the subcooling degree of the refrigerant at the condenser's end. This, in turn, significantly reduces the refrigerant dryness at the expansion valve outlet and evaporator inlet, greatly increasing the evaporator's cooling capacity and achieving deep subcooling for highly efficient dehumidification.

[0040] Compared to traditional dehumidifiers with ultra-low base efficiency, this invention achieves a significant improvement in dehumidification energy efficiency. This is because traditional dehumidifiers have a high refrigerant dryness at the evaporator inlet, typically around 0.35, with a liquid refrigerant percentage of around 0.65. This invention, through "deep subcooling" of the condensate, reduces the refrigerant dryness at the evaporator inlet to around 0.15, increasing the liquid refrigerant percentage to around 0.85. The increase in evaporator cooling and dehumidification capacity is not simply a matter of (0.85-0.65)×100%=20%, but rather requires comparing the traditional dehumidifier's "0.65" as a base. Using "deep subcooling" technology, the dehumidifier's evaporator cooling and dehumidification capacity are significantly increased by (0.85-0.65) / 0.65×100%=30.77%!

[0041] ② A heavy-duty two-stage assembly was constructed, achieving ultra-heavy load capability.

[0042] In this invention, the cooling, dehumidifying, and reheating airflow flows from the air inlet of the main unit to the air outlet, powered by a centrifugal fan, and undergoes two static pressure-dynamic pressure conversions to achieve high-speed intake by the centrifugal fan and high-speed exhaust from the exhaust chamber.

[0043] The ultra-high efficiency dehumidifier assembly of this invention uses at least two centrifugal fans mounted vertically on a wall to draw air from the negative pressure chamber of the dehumidifier assembly, creating a negative pressure inside the chamber. This negative pressure draws indoor ambient air at a static pressure of 0 Pa (gauge pressure) into the main unit at a medium speed (around 4 m / s) through the air inlet. The airflow is dispersed and slowed down by a multi-fin planer blade that cuts through the air inlet. It then flows through the gaps between the fins at a low speed (below 2 m / s) to complete heat exchange. After entering the negative pressure chamber, the airflow converges and accelerates, flowing at high speed into the centrifugal fan intake port, where the pressure is lowest (gauge pressure is negative), completing the first static pressure-dynamic pressure conversion. The high-speed airflow into the centrifugal fan intake port is pressurized by the fan and sent into the exhaust chamber, which has a positive pressure relative to the atmospheric environment. Under the action of the positive pressure in the exhaust chamber, the airflow is injected at high speed (around 8 m / s) from the small exhaust port into the indoor ambient air for diffusion and dilution.

[0044] This invention uses a fin planer to progressively plan the airflow into the main body, causing the airflow lines to enter and exit the fin gaps in a zigzag pattern within a plane perpendicular to the long side of the fins. This generates local resistances such as airflow impacting the fin tips and turning, airflow deceleration due to expansion of the flow cross-section within the fin gaps, and airflow acceleration due to turning at the exit of the fin gaps. The local resistance of the airflow entering and exiting the fin gaps is significantly greater than the resistance of the inlet section before the finned tube heat exchanger assembly and the resistance of the outlet section afterward. This makes the "throttling" effect of the fin gaps on the airflow more pronounced, thereby improving the uniformity of ventilation and heat transfer on the surface of the finned tube external heat exchanger assembly and increasing the heat transfer intensity. This enables the construction of a heavy-duty two-phase assembly and a heavy-duty dehumidifier.

[0045] In this invention, airflow resistance and convective heat transfer coefficient are a pair of "opposing and unified" heat exchange factors. Improving the convective heat transfer coefficient and heat transfer intensity usually comes at the cost of increasing flow resistance. The baffles in the shell and tube heat exchanger and the fin planer of this invention both improve the convective heat transfer coefficient and heat transfer intensity by increasing the necessary flow resistance. Attached Figure Description

[0046] Figure 1 This is a three-dimensional view of the heavy-duty, high-efficiency dual-super dehumidifier in Example 1.

[0047] Figure 2 Example 1 uses a pressure-enthalpy diagram to analyze the refrigerant cycle by increasing the subcooling of the refrigerant at the end of the condenser to reduce the vaporization ratio of the refrigerant in the throttle valve, thereby increasing the evaporation ratio of the refrigerant in the evaporator, and thus increasing the cooling capacity and dehumidification capacity.

[0048] Figure 3 This is a structural diagram of the end plate of the two-phase assembly submodule for improving the subcooling of the refrigerant at the end of the condenser to reduce the refrigerant vaporization ratio of the throttle valve, increase the cooling capacity of the evaporator, and improve the dehumidification efficiency in Example 1.

[0049] Figure 4 This is a structural diagram of the two-phase assembly of a dehumidifier in Example 1, which improves the subcooling of the refrigerant at the end of the condenser to reduce the refrigerant vaporization ratio of the throttling valve, increase the cooling capacity of the evaporator, and improve the dehumidification efficiency.

[0050] Figure 5 This is a top view of the structure of the ultra-high load, ultra-high energy efficiency dual-super dehumidifier in Example 1;

[0051] Figure 6 This is a top view of the airflow during operation of the two-unit assembly of the ultra-high load ultra-high energy efficiency dual ultra-dehumidifier in Example 1;

[0052] Figure 7 The horizontal cross-sectional view of the ultra-high efficiency dehumidifier in Example 1, where the "fin planer" at the inlet of the fin gap between the two assemblies is used to plan the airflow in stages, causing it to slow down and pass through the fin gap;

[0053] Figure 8 This is a top view of the structure of the ultra-high load, ultra-high energy efficiency dual-super dehumidifier with the exhaust chamber expanded into the compressor chamber in Example 2;

[0054] Figure 9 This is a top view of the airflow during operation of the ultra-high load, ultra-high energy efficiency dual-super dehumidifier with the exhaust chamber expanded into the compressor chamber in Example 2.

[0055] Figure 10 This is a top view of the fan wall-mounted dehumidifier structure using a three-finned tube assembly in Example 3;

[0056] Figure 11 This is a top view of the airflow during operation of the front-mounted dehumidifier using a three-finned tube assembly in Example 3.

[0057] Figure 12 This is a top view of the structure of the ultra-high load, ultra-high energy efficiency dual-super dehumidifier in Example 4;

[0058] Figure 13 This is a top view of the airflow during operation of the ultra-high load, ultra-high energy efficiency dual-super dehumidifier in Example 4;

[0059] Figure 14 This is a vertical cross-sectional view of the airflow during operation of the heavy-duty, ultra-high-efficiency dual ultra-dehumidifier, which includes a dual refrigeration and dehumidification system, as shown in Example 5. Detailed Implementation

[0060] To make the objectives, technical solutions, and advantages of this application clearer, the technical solutions of this application will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some, not all, of the embodiments of this application. All other embodiments obtained by those skilled in the art based on the described embodiments without creative effort are within the scope of protection of this application.

[0061] Unless otherwise defined, the technical or scientific terms used in this application shall have the ordinary meaning understood by one of ordinary skill in the art to which this application pertains. The terms "first," "second," and similar terms used in this application do not indicate any order, quantity, or importance, but are merely used to distinguish different components. Terms such as "comprising" or "including" mean that the element or object preceding the word encompasses the elements or objects listed following the word and their equivalents, without excluding other elements or objects. Terms such as "connected" or "linked" are not limited to physical or mechanical connections, but can include electrical connections, whether direct or indirect.

[0062] In the description of this invention, it should be understood that the terms "lateral", "longitudinal", "length", "up", "down", "left", "right", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0063] Definition: The direction perpendicular to the exterior facade of the external corridor equipment platform is defined as longitudinal, and the direction parallel to the exterior facade of the external corridor equipment platform is defined as transverse.

[0064] Example 1

[0065] like Figure 1-7 As shown, a heavy-duty, high-efficiency dehumidifier includes a housing 1, a dehumidifier assembly 2, a compressor 3, and an exhaust chamber 4. A negative pressure chamber 5 is composed of the dehumidifier assembly 2, a portion of the housing 1, and a back plate 51. Each negative pressure chamber 5 has two air outlets 52 on its back plate 51, each outlet 52 equipped with a vertically arranged fan 6. The dehumidifier assembly 2 is located on the air inlet surface 11 of the housing 1, serving as the air inlet for the negative pressure chamber 5. The air outlets 52 on the back plate 51 correspond to the air intakes of the vertically arranged fans 6. The air outlets 52 connect to the exhaust chamber 4. The exhaust port 41 of the exhaust chamber 4 is located on the top plate 13 of the housing 1.

[0066] The housing 1 contains two sets of dehumidifier assemblies 2 and two negative pressure chambers 5; the housing 1 also contains a compressor chamber 31, which houses the compressor 3 and the electrical box.

[0067] Each negative pressure chamber 5 has a back plate 51 with two air outlets 52; each air outlet 52 is equipped with a fan 6, forming a fan wall; the fan 6 is a backward-inclined external rotor centrifugal fan.

[0068] The exhaust chamber 4 is composed of a side plate 12, a top plate 13 and a bottom plate (not shown) of the housing 1, a back plate 51 of the negative pressure chamber 5, and an exhaust chamber back plate; the exhaust port 41 of the exhaust chamber 4 is a rectangular exhaust port.

[0069] The exhaust surface enclosed by the exhaust port 41 is located on the top plate 13 of the long side of the housing 1, and the air inlet surface 11 is located on the front of the housing 1.

[0070] A water tank for collecting condensate is provided below the exhaust chamber 4 and / or the negative pressure chamber 5.

[0071] The compressor chamber 31 is located between the two dehumidifier assemblies 2. The compressor chamber 31 is used to house the refrigerant circuit assembly, which includes the compressor 3, gas-liquid separator, four-way valve, expansion valve, and electrical box.

[0072] The dehumidifier assembly 2 is a horizontal cross-section V-shaped dual-unit combination module 22 consisting of two dual-unit combination modules 21; the long side of the fins 23 of the dual-unit combination module 21 is arranged in the vertical direction or close to the vertical direction in the horizontal air duct; the horizontal cross-section of the dehumidifier assembly 2 perpendicular to the long side of the fins 23 is a sawtooth-shaped zigzag.

[0073] The two-unit combination module 22 includes a condenser 24 and an evaporator 28. The condenser 24 includes a superheated heat release section 25, a condensing section 26 and a subcooling section 27. The superheated heat release section 25, the condensing section 26, the subcooling section 27 and the evaporator 28 are all flat plate finned tube heat exchangers.

[0074] The horizontal cross-section of the dehumidifier assembly 2, which is perpendicular to the long side of the fins 23, is V-shaped.

[0075] The apex angle α of the horizontal cross-section V-shaped two-electrode combination module 22 is 15° to 110°.

[0076] The apex angle α of the horizontal cross-section V-shaped two-electrode combination module 22 is 30° to 90°.

[0077] In one preferred embodiment, the apex angle α of the horizontal cross-section V-shaped two-electrode combination module 22 is 30° to 60°.

[0078] The horizontal cross-section of the dehumidifier assembly 2, which is perpendicular to the long side of the fin 23, is the air inlet side of the heat exchanger (i.e., the air inlet side of the dehumidifier assembly) on one side, and the air outlet side of the heat exchanger (i.e., the air outlet side of the dehumidifier assembly) on the other side.

[0079] The incident surface of the airflow is the flat plate finned tube heat exchanger of each two-unit combination module 21. The angle between the airflow and the tip of each fin on each flat plate finned tube heat exchanger is an obtuse angle; the obtuse angle β is 97.5° to 145°.

[0080] The incoming airflow impacts the tip of each fin in the flat plate finned tube heat exchanger at an obtuse angle β, and is reflected by the fin tip plate into the fin gap and flows into the negative pressure chamber 5.

[0081] The airflow rate entering each fin gap d is equal to the airflow intercepted by the vertical distance δ between the tips of the two fins on the air inlet section of the flat plate finned tube heat exchanger.

[0082] δ=d·sinα / 2, where α is the apex angle of the horizontal cross-section V-shaped two-electrode combination module 22;

[0083] The vertical distance δ between the tips of the front and rear fins of the flat plate finned tube heat exchanger on the air inlet section is between 0.13d and 0.7d; the airflow velocity between the fins is 1 / 3 of the air inlet velocity, corresponding to the apex angle α of the horizontal cross-section V-shaped two-unit combined module 22 being 39° and the incident obtuse angle β being 109.5°.

[0084] Evaporator 28 and condenser 24 include fins 23 and heat exchange tubes 29; multiple parallel fins 23 with a certain distance between them form a fin group; heat exchange tubes 29 are installed in a direction perpendicular to the plane of the fins 23.

[0085] Along the short side of the fin 23, several sets of heat exchange tubes 291 are arranged in parallel and parallel to each other and pass through the fin 23.

[0086] The heat exchange tubes 29 in the heat exchange tube assembly 291 are arranged along the long side of the fins 23.

[0087] Heat exchange tube 29 and heat exchange tube assembly 291 are equivalent to refrigerant piping or refrigerant sub-pipes.

[0088] Evaporator 28, subcooling section 27, and condensing section 26 are arranged adjacent to each other, with evaporator 28 embedded in condenser 24; superheated heat release section 25 is located above the parallel-arranged evaporator 28, subcooling section 27, and condensing section 26; subcooling section 27 is located between condensing section 26 and evaporator 28. The refrigerant lines of superheated heat release section 25, condensing section 26, and subcooling section 27 are connected in series; the output end of subcooling section 27 of condenser 24 is connected to the input end of evaporator 28 through a throttling device.

[0089] The refrigerant pipeline outlet of the subcooling section 27 is connected to the refrigerant pipeline inlet of the evaporator 28 through a throttling device; the refrigerant pipeline of the evaporator 28 includes 4 parallel refrigerant sub-pipelines, and the refrigerant pipeline outlet of the subcooling section 27 is connected to the inlet of each of the 4 refrigerant sub-pipelines through a throttling device.

[0090] The refrigerant piping of the superheated heat release section 25 includes two parallel refrigerant sub-pipes, which are arranged vertically.

[0091] The refrigerant sub-pipes of the superheated heat release section 25 are connected in series to the refrigerant sub-pipes of the condensing section 26. The two refrigerant sub-pipes of the condensing section 26 are arranged side by side, and the two refrigerant sub-pipes are arranged in a cross pattern, with their left and right positions interchanged;

[0092] The refrigerant sub-pipes arranged side by side in the evaporator 28 are arranged in a cross pattern, and their left and right positions are swapped.

[0093] This embodiment of the heavy-duty, high-efficiency dehumidifier aims to improve the dehumidification efficiency ratio and cooling load intensity of the dehumidifier. Based on thermodynamics, it restructures the dehumidifier's two components (evaporator and condenser) and the refrigerant circuit, as well as the airflow path, re-coupling the refrigerant and airflow paths. It employs an evaporator-condenser submodule with high airflow, low condensing pressure, deep subcooling, and high-efficiency dehumidification as the structural unit of the dehumidifier's two-component assembly, constructing a dehumidifier assembly with heavy-duty, high-efficiency characteristics. Furthermore, this embodiment promotes a same-layer, complementary design between the compressor chamber and the exhaust chamber, placing the compressor between the two dehumidifier assemblies, expanding the exhaust chamber, and eliminating ventilation blind spots and ineffective spaces within the dehumidifier structure.

[0094] The technical objective of this ultra-high efficiency dehumidifier for heavy-duty applications is to analyze the operational status of dehumidifiers in indoor spaces such as basements, warehouses, workshops, and residences, and to pursue the limits of energy efficiency ratio and load intensity of refrigeration dehumidification technology. The dehumidifier operates in an indoor environment where, apart from slightly high humidity, temperature, cleanliness, and other environmental indicators are moderate, stable, and controllable. The globally accepted standard test condition for dehumidifier performance is set at 27°C 60% (26.7°C 60% in the US and Europe, with 26.7°C converted from 80°F), confirming the typical operating environment for dehumidifiers. Under the standard condition of 27°C 60%, the density, enthalpy, viscosity, and other physical properties of the air are relatively moderate, which is conducive to significantly improving the dehumidification efficiency of the dehumidifier, reaching over 3.5L H2O / kWh. It also helps to significantly increase the cooling load intensity of the dehumidifier, reducing the main unit volume occupied by each 1L H2O / h dehumidification capacity to below 50L.

[0095] This embodiment refines and integrates the technical goal of ultra-high energy efficiency under heavy load into the refrigerant-side optimized matching design, airflow-side optimized matching design, electromechanical structure design, and operational process optimization design of the dehumidifier's refrigeration system.

[0096] ①The core requirement for system matching is to "reduce the refrigerant two-phase flow dryness at the outlet of the throttling valve".

[0097] The dehumidification capacity of a dehumidifier depends on the cooling capacity of its evaporator, which is the product of the refrigerant circulation rate and the enthalpy difference between the refrigerant at the inlet and outlet of the evaporator. This enthalpy difference is negatively correlated with the "dryness" of the refrigerant entering the evaporator from the outlet of the expansion valve.

[0098] The refrigerant dryness fraction at the evaporator inlet refers to the proportion of gaseous refrigerant at the outlet of the expansion valve in the gas-liquid two-phase flow of the refrigerant. The lower the dryness fraction, the closer it is to 0, meaning a low gaseous proportion (close to 0) and a high liquid proportion (close to 1.0). This results in a higher degree of "completeness" of refrigerant evaporation in the evaporator, a larger enthalpy difference between the inlet and outlet of the evaporator, and thus a larger evaporator cooling capacity and dehumidification capacity. Conversely, the higher the refrigerant dryness fraction at the evaporator inlet, the closer it is to 1, meaning a high gaseous proportion (close to 1) and a low liquid proportion (close to 0). This results in a lower degree of "completeness" of refrigerant evaporation in the evaporator, a smaller enthalpy difference between the inlet and outlet of the evaporator, and thus a smaller cooling capacity and dehumidification capacity.

[0099] The refrigerant "dryness" at the outlet of the expansion valve, i.e., the inlet of the evaporator, is determined by the "subcooling" of the refrigerant at the end of the condenser. During the throttling and depressurization process of the refrigerant in the expansion valve, in order to reduce the temperature of the high-pressure, high-temperature refrigerant condensate at the condenser outlet, i.e., the inlet of expansion valve 222, to the saturation temperature corresponding to the low-pressure state at the expansion valve outlet, i.e., the inlet of the evaporator, a portion of the refrigerant condensate vaporizes during the throttling process. The heat absorbed by the vaporization of a small portion of the condensate cools most of the condensate, resulting in the refrigerant injected into the evaporator inlet from the outlet of the expansion valve not being a liquid refrigerant with a dryness of 0, but rather a gas-liquid two-phase flow with a dryness of x. The dryness of x can be 0.2 (liquid percentage 0.8), 0.3 (liquid percentage 0.7), 0.4 (liquid percentage 0.6), or even 0.5 (liquid percentage 0.5).

[0100] The refrigerant dryness fraction (x) at the outlet of the expansion valve and the inlet of the evaporator in a dehumidifier is determined by the "subcooling" of the condensate at the end of the condenser. If the condensate at the end of the condenser releases heat sufficiently and its temperature drops significantly (significantly below the condensation temperature), it has a high "subcooling." As the condensate enters the evaporator through expansion valve 222, the temperature difference between the condensate at the end of the condenser and the evaporation temperature is small, resulting in less heat release. Consequently, the proportion of refrigerant undergoing a phase change and absorbing heat through vaporization in the expansion valve is relatively low. Therefore, the refrigerant dryness fraction (x) at the outlet of the expansion valve, i.e., the inlet of the evaporator, is correspondingly low, sometimes as low as 0.2 or even below. This results in a relatively high proportion of liquid phase in the two-phase flow of the refrigerant entering the evaporator. When the evaporator is in a subcooled state, its cooling and dehumidification capacity is relatively large. Conversely, if the condensate at the condenser terminal does not release heat sufficiently and its temperature is too high (not significantly lower than the condensing temperature), meaning the condensate has a low "subcooling," the temperature difference between the condensate at the condenser terminal and the evaporating temperature is large, resulting in a large amount of heat release. Consequently, the proportion of condensate undergoing a "phase change" and vaporizing to absorb heat when passing through the condenser is relatively high. The refrigerant dryness fraction (x) at the condenser outlet (i.e., the evaporator inlet) is correspondingly high, reaching 0.3 or even above 0.4. This results in a relatively low proportion of liquid phase in the two-phase flow of refrigerant entering the evaporator, leading to a smaller cooling and dehumidification capacity.

[0101] Therefore, the ultra-high load and ultra-high energy efficiency dehumidifier of this embodiment is designed with the core concept of "reducing the dryness of the two-phase flow of refrigerant at the outlet of the throttling valve" in mind. It fully utilizes the cooling and subcooling effect of the low-temperature air outlet of the evaporator on the condensate at the end of the condenser, increases the subcooling of the condensate at the end of the condenser, reduces the vaporization ratio of the condensate in the throttling valve, reduces the dryness of the two-phase flow of refrigerant at the outlet of the throttling valve, increases the liquid phase ratio of the refrigerant at the inlet of the evaporator, and increases the cooling capacity and dehumidification capacity of the evaporator.

[0102] ② Innovative Structure of Ultra-High Energy Efficiency Dehumidifier

[0103] The ultra-high load and ultra-high energy efficiency dehumidifier in this embodiment starts from the refrigeration cycle of the refrigerant pressure-enthalpy diagram and uses a two-unit combination module of high-efficiency evaporator and condenser to construct the dehumidifier assembly;

[0104] The high-efficiency dehumidifier evaporator-condenser combination module used in this embodiment of the dehumidifier assembly essentially utilizes the low-temperature air outlet of the evaporator to achieve deep subcooling of the refrigerant at the end of the condenser, thereby reducing the dryness of the two-phase flow of refrigerant at the outlet of the expansion valve.

[0105] This embodiment of the ultra-high load and ultra-high efficiency dehumidifier assembly features an evaporator and condenser arranged side-by-side. The condenser is divided into three sections connected in series, corresponding to the high-temperature sensible heat release (i.e., superheated heat release section), latent heat release (i.e., condensation section), and subcooled heat release (i.e., subcooled section) of the refrigerant gas discharged from the compressor at high temperature and high pressure. This exploits the potential of the dehumidifier's evaporator's low-temperature exhaust air after "dehumidification." The cold exhaust air from the evaporator is directed directly towards the end of the condenser (i.e., the subcooled section), which is responsible for the subcooling heat release of the condensate. Furthermore, the thermal bridge between the end of the condenser (responsible for subcooling heat release) and the middle section (i.e., the condensation section), which is responsible for condensation heat release, is severed. This blocks the transfer of heat from the high-temperature condensation section to the subcooled section at the end of the condenser, significantly increasing the subcooling degree of the refrigerant at the end of the condenser. Consequently, the refrigerant dryness at the outlet of the expansion valve, i.e., the inlet of the evaporator, is significantly reduced, greatly increasing the evaporator's cooling capacity and dehumidification capacity, thus implementing deep subcooling and high-efficiency dehumidification.

[0106] This embodiment of the ultra-high load and ultra-high energy efficiency dehumidifier uses a two-unit combination module of high-efficiency evaporator and condenser to construct the dehumidifier two-unit assembly: the two-unit combination modules of two high-efficiency evaporator and condenser are combined to form one horizontal cross-section V-shaped two-unit combination module, and the two horizontal cross-section V-shaped two-unit combination modules are combined again to form the high-efficiency evaporator and condenser assembly; the horizontal cross-section of the dehumidifier two-unit assembly perpendicular to the long side of the fins has a sawtooth-shaped broken line horizontal cross-section.

[0107] In this embodiment, within the limited space of the dehumidifier, two horizontally cross-section V-shaped evaporator-condenser combination modules are arranged parallel to the air inlet surface of the main unit on one side. These modules are unfolded along the air inlet surface to obtain a large area of ​​high-efficiency evaporator-condenser combination module ventilation surface. The modules are then further unfolded on the ventilation surface to obtain a huge area of ​​fin heat transfer surface. This effectively increases the total heat transfer area of ​​the fins of the dehumidifier's two-phase assembly, reduces the heat transfer temperature difference between the evaporator and condenser bodies, increases the evaporation pressure, reduces the condensation pressure, and improves the cooling capacity and energy efficiency ratio of the dehumidifier's refrigeration system.

[0108] This embodiment of the ultra-high load and ultra-high energy efficiency dehumidifier is equipped with two negative pressure chambers 5 for the dehumidifier assemblies. Each negative pressure chamber 5 is composed of a base plate, side plates, a back plate, the dehumidifier assemblies, and a top plate. The dehumidifier assemblies are arranged horizontally and continuously on the back plate. The back plate has air outlets for the upper and lower negative pressure chambers. A backward-curved external rotor centrifugal fan is installed at the air outlet on the back plate. The air outlet on the back plate is also the air inlet of the backward-curved external rotor centrifugal fan. The back plate with multiple backward-curved external rotor centrifugal fans at the air outlets of multiple negative pressure chambers forms a wall surface for the backward-curved external rotor centrifugal fan. An exhaust chamber for the centrifugal fan is set on the outside of the backward-curved external rotor centrifugal fan wall. The exhaust chamber is composed of the fan wall surface, side plates, upper and lower bottom surfaces, and outer surface. The air outlet of the exhaust chamber is located on the top plate of the exhaust chamber. Between the dehumidifier assemblies, a compressor chamber is set up to house the dehumidifier compressor, expansion valve, electrical box, and other refrigerant circuit components.

[0109] ③ Innovative design of the inlet and outlet airflow of the dehumidifier's two-phase assembly

[0110] In this embodiment, during the ventilation and heat exchange operation of the two-unit assembly of an ultra-high load and ultra-high efficiency dehumidifier, the airflow from the main unit's air inlet to the exhaust outlet undergoes two static-to-dynamic pressure conversions, powered by a centrifugal fan. The first static-to-dynamic pressure conversion enables high-speed airflow intake at the centrifugal fan's air inlet, and the second static-to-dynamic pressure conversion enables high-speed airflow exhaust at the exhaust outlet. Furthermore, the airflow lines entering and exiting the fin gap of the two-unit assembly in this embodiment are zigzag airflow lines with two bends, located in a plane perpendicular to the long side of the fins, rather than in a plane parallel to the fins. These two points are the most essential motion characteristics of the ventilation and heat exchange process of the two-unit assembly of the dehumidifier in this embodiment.

[0111] This embodiment establishes the airflow field for the dehumidifier's two-phase assembly by operating multiple centrifugal fans on the fan wall: at least two centrifugal fans on the vertically arranged fan wall draw air from the negative pressure chamber of the dehumidifier's two-phase assembly, creating negative pressure within the chamber. This negative pressure draws ambient air at 0 Pa static pressure (gauge pressure) into the main unit at a medium speed (approximately 4 m / s) through the air inlet. The airflow is dispersed and slowed down by planing the airflow through multiple fins, then flows at a low speed (below 2 m / s) through the gaps between the fins of the dehumidifier's two-phase assembly to complete heat exchange. Afterward, the air enters the negative pressure chamber, where it converges and accelerates. The airflow flows at high speed into the centrifugal fan intake port, which has the lowest pressure (negative gauge pressure) along the entire path, completing the first static-dynamic pressure conversion. The high-speed airflow flowing into the centrifugal fan intake port is pressurized by the fan and sent into the exhaust chamber, which has a positive pressure relative to the atmospheric environment. Under the positive pressure of the exhaust chamber, it is injected into the ambient air at high speed (about 8m / s) from the small rectangular exhaust port on the outer surface of the exhaust chamber for diffusion and dilution. In this embodiment, the heat exchange airflow from the main unit intake port to the exhaust port, powered by the centrifugal fan, undergoes two static-dynamic pressure conversions to achieve high-speed intake of the centrifugal fan and high-speed exhaust from the exhaust chamber.

[0112] In this embodiment, the microscopic process of airflow entering and exiting the fin gap and flowing at low speed in the fin gap during the operation of the dehumidifier is an important part of the airflow field of the dehumidifier's two-phase assembly.

[0113] At the airflow inlet section EE, the medium-speed airflow of about 4 m / s, flowing in from the outer facade of the equipment platform, is propelled in a uniform laminar flow to the fin gap inlet section FF. At FF, the airflow line at the inlet forms an obtuse angle with the fin behind the gap. The fin behind the gap acts as a "planer," "planing" a piece of airflow from the main airflow and inserting it into the fin gap. At FF, the main airflow "planed" out by the tip of the "fin planer" is intercepted and impacts the tip of the "planer" on the fin behind the gap at an obtuse angle. After being reflected by the fin in front of the gap, it diffuses and decelerates in the fin gap. The airflow of about 1.5 m / s, which has been decelerated by the collision and diffusion, is pulled by the negative pressure of the negative pressure chamber and overcomes the resistance of the fin gap channel to flow out of the fin channel. The low-speed airflow that reaches the fin gap outlet section GG is accelerated again to a medium-speed airflow of about 4 m / s under the negative pressure of the negative pressure chamber and converges and is discharged at the HH section.

[0114] During operation of the high-efficiency dehumidifier in this embodiment, heat exchange occurs between the refrigerant inside the evaporator-condenser pipes and the airflow between the fins outside the pipes, thus achieving energy coupling.

[0115] In this embodiment, on the refrigerant side, the refrigerant is driven to circulate by a compressor, and the heat is generated by the high-efficiency phase change of the refrigerant during the circulation process, so as to couple the heat absorption of the evaporator and the heat release of the condenser.

[0116] In this embodiment, a compressor chamber is set outside the two-phase assembly of the dehumidifier (i.e., between the two dehumidifier assemblies), where refrigeration circuit components such as the compressor, expansion valve, and gas-liquid separator, as well as circuit components such as power cables, signal lines, and electrical boxes, are housed. These refrigeration circuit components, along with the two-phase assembly, refrigerant connecting pipes, and other components, form the dehumidifier refrigeration cycle circuit in the order of compressor-condenser-expansion valve-evaporator-compressor. The compressor, as the power source of the refrigeration cycle circuit, establishes high and low pressure states for the refrigerant in the condenser and evaporator pipes, driving the refrigerant to circulate and undergo repeated phase changes in the refrigeration cycle circuit to achieve "heat transfer." That is, the refrigerant liquid evaporates and absorbs heat in the evaporator pipes, and then absorbs the heat from the ambient air flowing between the fins through the large heat-absorbing area of ​​the copper tubes to achieve "cooling and dehumidification." Then, the high-temperature and high-pressure refrigerant gas condenses and releases heat in the condenser pipes, and then releases heat to the ambient air flowing between the fins through the large heat-releasing area of ​​the copper tubes. This achieves the migration of heat from the air being cooled and dehumidified by the dehumidifier evaporator to the "reheated" air after dehumidification by the condenser.

[0117] Example 2

[0118] like Figure 8-9As shown, this embodiment differs from Embodiment 1 in that the dehumidifier assemblies 2 on both sides of the dehumidifier are both horizontal cross-section V-shaped two-unit combination modules 22, which have high energy density and load strength. In order to expand the exhaust chamber 4 and the exhaust port 41, the exhaust chamber 4 and the exhaust port 41 are expanded above the compressor chamber 31, and the exhaust chamber 41 and the exhaust port have a T-shaped structure.

[0119] This embodiment employs a co-layered and complementary design of the compressor chamber 31 and the exhaust chamber 4, placing the compressor 3 between the two dehumidifier assemblies 2 and reducing the space of the compressor chamber 31. This further extends the exhaust chamber 4 into the compressor chamber 31, completely eliminating ventilation blind spots and ineffective spaces within the dehumidifier structure, thus further improving the dehumidification efficiency ratio. The dehumidification efficiency ratio of this embodiment approaches the theoretical limit of 3.5L H2O / kWh for refrigeration dehumidification technology under standard operating conditions of 27℃ and 60%, achieving ultra-high dehumidification efficiency. Furthermore, the heat exchange intensity is further improved in this embodiment, constructing a heavy-duty dehumidifier assembly and a heavy-duty dehumidifier, with each 1L H2O / h dehumidification capacity occupying less than 50L of dehumidifier volume.

[0120] Example 3

[0121] like Figure 10-11 As shown, this embodiment has the same principle and structure as embodiment 1. The air inlet, dehumidifier assembly 2, negative pressure chamber 5, fan wall, and vertical exhaust chamber are arranged in a linear progression, with the compressor chamber 31 located in the middle.

[0122] The difference in this embodiment is that the dehumidifier assembly 2 is composed of three two-unit combination modules 21 (i.e., flat plate finned tube heat exchangers); two of the two-unit combination modules 21 form a horizontal cross-section V-shaped two-unit combination module 22; the other two-unit combination module 21 (i.e., flat plate finned tube heat exchanger) is independently arranged on the outside of the horizontal cross-section V-shaped two-unit combination module 22, and a partition 223 perpendicular to the air inlet surface is provided between the partition 223 and the horizontal cross-section V-shaped two-unit combination module 22. The space between the partition 223 and the two-unit combination module 21 is the negative pressure chamber of the two-unit combination module 21.

[0123] In this embodiment, the heat exchange area can be appropriately increased by using a three-piece two-phase combination module 21 with a V+1 structure as the two-phase assembly 2 of the dehumidifier, compared with a single horizontal cross-section V-shaped two-phase combination module 22, to meet the needs of a dehumidifier with a larger cooling and dehumidification capacity.

[0124] Example 4

[0125] like Figure 12-13 As shown, the difference between this embodiment and embodiment 1 is that the two dehumidifier assemblies 2 on both sides of the dehumidifier are both W-shaped structures with a horizontal cross-section perpendicular to the long side of the fins, resulting in higher energy density and load strength.

[0126] In this embodiment, the compressor chamber 31 and the exhaust chamber 4 are designed in the same layer and complement each other. The compressor 3 is placed between the two dehumidifier assemblies 2, which expands the exhaust chamber and eliminates the ventilation blind spots and ineffective spaces inside the dehumidifier structure, thereby further improving the dehumidification energy efficiency ratio and dehumidification load intensity.

[0127] Example 5

[0128] like Figure 14 As shown, the difference between this embodiment and embodiment 1 is that the ultra-high energy efficiency and heavy load dehumidifier is equipped with two refrigeration systems, namely, two refrigeration and dehumidification systems consisting of two independent compressors 3, condensers 24, expansion valves 222, and evaporators 28.

[0129] In this embodiment, the superheated heat release section 25 of the two condensers 24, the condensing section 26 of the two condensers, the subcooling section 27 of the two condensers, and the two evaporators 28 of the two refrigeration and dehumidification systems are arranged adjacently or even embedded in each other, forming pairs, and each pair shares a set of fins. That is, the refrigerant piping of the superheated heat release section 25 of the two condensers 24 shares a set of fins, the refrigerant piping of the condensing section 26 of the two condensers shares a set of fins, the refrigerant piping of the subcooling section 27 of the two condensers shares a set of fins, and the refrigerant piping of the two evaporators 28 shares a set of fins. Each set of fins in the superheated heat release section 25, the condensing section 26, the subcooling section 27, and the evaporator 28 forms a fin thermal bridge for the refrigerant piping of the two refrigeration systems, but the thermal bridge connection between the sets of fins is disconnected.

[0130] On the fins, finned thermal bridges are provided between the heat exchange tube groups in the superheated heat release section, which belongs to each refrigeration and dehumidification system and is arranged adjacently, to form a superheated heat release section combination; finned thermal bridges are provided between the heat exchange tube groups in the condensing section, which belongs to each refrigeration and dehumidification system and is arranged adjacently, to form a condensing section combination; finned thermal bridges are provided between the heat exchange tube groups in the subcooling section, which belongs to each refrigeration and dehumidification system and is arranged adjacently, to form a subcooling section combination; finned thermal bridges are provided between the heat exchange tube groups in the evaporator, which belongs to each refrigeration and dehumidification system and is arranged adjacently, to form an evaporator combination;

[0131] On the fins, longitudinal and / or transverse gaps are provided between the superheated heat release section, condensing section, subcooling section and evaporator in the two-phase module to cut off the thermal bridges of the fins, and longitudinal and / or transverse fin ribs are provided to fix the relative spatial structural relationship of each area of ​​the fins.

[0132] During the refrigeration and dehumidification operation in this embodiment, the following occurs: Figure 14From the airflow side, the airflow to be dehumidified flows from left to right under the drive of the fan. The main airflow in the lower middle part of the air duct passes through the evaporator for cooling and dehumidification, the condenser section of the condenser, and the subcooling section for heating and reheating to become dry air before being discharged from the dehumidifier. From the refrigerant side, the refrigerant gas discharged from the compressor on the left is discharged into the black pipe in the superheated heat release section of the condenser through the pipe shown by the solid line. It continues to release heat in the black pipe in the superheated heat release section of the condenser, continuously moving up and down and from right to left to the outlet of the pipe in the lower left corner, and is discharged into the top rightmost black pipe in the condenser section of the condenser for condensation and heat release. It moves downward and is discharged from the bottom rightmost black pipe, then passes through a large-span black pipe and is sent upward into the subcooling section of the condenser. It continues to release heat and undergoes deep subcooling in the subcooling section of the condenser, then enters the expansion valve (capillary tube) for pressure reduction, and is then sent into the evaporator in the upper and lower sections of the black pipe for evaporation and heat absorption to become low-pressure refrigerant gas. It is then sucked into the compressor, pressurized, and discharged into the superheated heat release section of the condenser to start the next cycle.

[0133] In this embodiment, the superheated heat release section, condensing section, subcooling section, and evaporator of the two condensers in the two refrigeration and dehumidification systems are grouped in pairs and share a set of fins to form heat exchanger modules with fin thermal bridges. When only one of the two refrigeration systems is running dehumidification, the dehumidification system significantly increases the fin heat exchange area of ​​the evaporator and condenser by utilizing the fins of the evaporator and condenser of the other refrigeration system, thereby significantly reducing the heat transfer temperature difference between the evaporator and condenser and significantly improving the dehumidification energy efficiency ratio.

[0134] Obviously, the above embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the implementation of the present invention. Those skilled in the art can make other variations or modifications based on the above description. It is neither necessary nor possible to exhaustively describe all embodiments here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the scope of protection of the claims of the present invention.

Claims

1. A heavy-duty, high-efficiency dehumidifier, characterized in that, It includes a housing, a dehumidifier assembly, a compressor, and an exhaust chamber; the negative pressure chamber is composed of the dehumidifier assembly, a bottom plate, a side plate, a top plate, and a back plate; the back plate is provided with several air outlets of the negative pressure chamber, and the air outlets are equipped with vertically arranged fans; The dehumidifier assembly is located on the air inlet side of the housing, and the dehumidifier assembly serves as the air inlet of the negative pressure chamber; The air outlet on the back panel corresponds to the air intake of the vertically arranged fan; the air outlet is connected to the exhaust chamber; the exhaust port of the exhaust chamber is located on the side panel, top panel, or back panel of the housing. The housing contains two sets of dehumidifier assemblies and two negative pressure chambers; The housing contains a compressor chamber that houses the compressor and an electrical box; The dehumidifier assembly is composed of a horizontal cross-section V-shaped dual-unit combination module consisting of at least two dual-unit combination modules; or it is composed of a dual-unit combination module and the horizontal cross-section V-shaped dual-unit combination module; or it is composed of one or two of the dual-unit combination module and the horizontal cross-section V-shaped dual-unit combination module, along with several partitions. The long side of the fins of the two-unit combination module is arranged in the vertical direction in the horizontal air duct; the horizontal cross section of the two-unit assembly of the dehumidifier perpendicular to the long side of the fins is a sawtooth-shaped zigzag. The two-evapor combination module includes a condenser and an evaporator. The condenser includes a superheated heat release section, a condensing section, and a subcooling section. The superheated heat release section, the condensing section, the subcooling section, and the evaporator are all flat plate finned tube heat exchangers. The dehumidifier's two-phase assembly has its air inlet side on one side of the horizontal cross-section perpendicular to the long side of the fins, and its air outlet side on the other side. The airflow incident surface is the flat plate finned tube heat exchanger of each two-unit combination module, and the angle between the airflow and the tip of each fin on each flat plate finned tube heat exchanger is an obtuse angle. The incoming airflow impacts the tip of each fin in the flat-plate finned tube heat exchanger at an obtuse angle β, and is reflected by the fin tip plate into the fin gap and flows into the negative pressure chamber; the obtuse angle β is 97.5° to 145°. The airflow rate entering each fin gap d is equal to the airflow intercepted by the vertical distance δ between the tips of the two fins on the air inlet section of the flat plate finned tube heat exchanger; δ=d·sinα / 2, where α is the apex angle of the horizontal cross-section V-shaped two-unit combined module.

2. The ultra-heavy-duty, ultra-high-efficiency dehumidifier according to claim 1, characterized in that, The compressor chamber is located between the two sets of dehumidifier assemblies, or on one side of the dehumidifier assemblies.

3. The ultra-high efficiency dehumidifier for heavy-duty applications according to claim 1, characterized in that, The exhaust port of the exhaust chamber is located on the top plate of the casing.

4. The ultra-high energy efficiency dehumidifier for heavy-duty applications according to claim 1, characterized in that, The back panel is provided with at least two air outlets; each air outlet is equipped with a fan, forming a fan wall.

5. The ultra-high energy efficiency dehumidifier with heavy load capacity according to claim 4, characterized in that, The fan is either a centrifugal fan or an axial flow fan.

6. The ultra-heavy-duty, ultra-high-efficiency dehumidifier according to claim 1, characterized in that, The exhaust chamber is composed of a side plate of the housing, a bottom plate, a back plate of the negative pressure chamber, and an exhaust chamber back plate.

7. The ultra-high efficiency dehumidifier for heavy-duty applications according to claim 6, characterized in that, The exhaust port of the exhaust chamber is a rectangular exhaust port.

8. The ultra-heavy-duty, ultra-high-efficiency dehumidifier according to claim 6, characterized in that, The exhaust surface enclosed by the exhaust port is located on the top plate of the housing or the back plate of the exhaust cavity, and the air inlet surface is located on the front side of the housing or / and the long side adjacent to the front side.

9. The ultra-high efficiency dehumidifier for heavy-duty applications according to claim 6, characterized in that, A compressor chamber, including a compressor and an electrical box, is provided on the outside of the exhaust chamber back plate, or on the outside of the negative pressure chamber, or below the exhaust chamber and / or the negative pressure chamber.

10. The ultra-high energy efficiency dehumidifier for heavy-duty applications according to claim 1, characterized in that, A water tank for collecting condensate is provided below the exhaust chamber and / or negative pressure chamber.

11. The ultra-high energy efficiency dehumidifier for heavy-duty applications according to claim 1, characterized in that, The dehumidifier assembly has a V-shaped or N-shaped horizontal cross-section perpendicular to the long side of the fins, or is composed of at least two V-shaped two-unit combination modules arranged continuously.

12. The ultra-heavy-duty, ultra-high-efficiency dehumidifier according to claim 11, characterized in that, The horizontal cross-section of the two-phase assembly of the dehumidifier, perpendicular to the long side of the fins, is W-shaped.

13. The ultra-heavy-duty, ultra-high-efficiency dehumidifier according to claim 11, characterized in that, The apex angle α of the horizontal cross-section V-shaped two-electrode combination module is 15° to 110°.

14. The ultra-high energy efficiency dehumidifier for heavy-duty applications according to claim 1, characterized in that, The vertical distance δ between the tips of the front and rear fins of a flat plate finned tube heat exchanger on the air inlet section is between 0.13d and 0.7d.

15. The ultra-heavy-duty, ultra-high-efficiency dehumidifier according to claim 14, characterized in that, The airflow velocity between the fins is 1 / 3 of the inlet velocity, corresponding to a apex angle α of 39° and an incident obtuse angle β of 109.5° for the V-shaped two-phase combined module with a horizontal cross section.

16. The ultra-high energy efficiency dehumidifier for heavy-duty applications according to claim 1, characterized in that, The evaporator, the subcooling section, and the condensing section are arranged adjacent to each other, with the evaporator embedded in the condenser; the superheated heat release section is located above the evaporator, the subcooling section, and / or the condensing section arranged side by side; the subcooling section is located between the condensing section and the evaporator.

17. The ultra-high energy efficiency dehumidifier for heavy-duty applications according to claim 1, characterized in that, The refrigerant piping of the superheated heat release section, condensing section, subcooling section and evaporator is connected in series. The output end of the subcooling section of the condenser is connected to the input end of the evaporator through a throttling device. The refrigerant piping of the evaporator includes at least two parallel refrigerant sub-pipelines. The output port of the refrigerant piping of the subcooling section is connected to the input ports of several of the refrigerant sub-pipelines through the throttling device.

18. The ultra-high efficiency dehumidifier for heavy-duty applications according to claim 1, characterized in that, The two-unit combination module is equipped with two sets of condensers and two sets of evaporators; the two sets of condensers and two sets of evaporators in the two-unit combination module belong to two independent refrigeration and dehumidification systems.

19. The ultra-heavy-duty, ultra-high-efficiency dehumidifier according to claim 18, characterized in that, Two condensers and two evaporators are mounted on the same finned assembly. On the fins, finned thermal bridges are provided between the heat exchange tube assemblies in the superheated heat release sections, which belong to each refrigeration and dehumidification system and are arranged adjacently, to form superheated heat release section combinations. Finned thermal bridges are also provided between the heat exchange tube assemblies in the condensing sections, which belong to each refrigeration and dehumidification system and are arranged adjacently, to form condensing section combinations. Finned thermal bridges are also provided between the heat exchange tube assemblies in the subcooling sections, which belong to each refrigeration and dehumidification system and are arranged adjacently, to form subcooling section combinations. Finally, finned thermal bridges are provided between the heat exchange tube assemblies in the evaporators, which belong to each refrigeration and dehumidification system and are arranged adjacently, to form evaporator combinations. On the fins, longitudinal and / or transverse gaps are provided between the superheated heat release section, condensing section, subcooling section and evaporator in the two-phase module to cut off the thermal bridges of the fins, and longitudinal and / or transverse fin ribs are provided to fix the relative spatial structural relationship of each area of ​​the fins.

20. The ultra-heavy-duty ultra-high-efficiency dehumidifier according to claim 19, characterized in that, The superheated heat release section, condensing section, subcooling section and evaporator are each composed of multiple refrigerant pipeline branches connected in parallel, and the heat exchange tube groups of each refrigerant pipeline branch are arranged side by side.

21. The ultra-heavy-duty, ultra-high-efficiency dehumidifier according to claim 20, characterized in that, The heat exchange tube bundles are arranged alternately side by side.

22. The ultra-high energy efficiency dehumidifier for heavy-duty applications according to claim 1, characterized in that, The exhaust chamber and exhaust port are expanded into the compressor chamber, and the exhaust chamber and exhaust port have a T-shaped structure.

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