A dehumidifier device assembly and its ultra-high energy efficiency dehumidifier

Abstract

This invention belongs to the field of new energy technology and discloses a dehumidifier two-phase assembly and its ultra-high energy efficiency dehumidifier. The dehumidifier two-phase assembly is a horizontal cross-section V-shaped two-phase assembly module consisting of at least two two-phase assembly modules; or a structure consisting of two-phase assembly modules and a horizontal cross-section V-shaped two-phase assembly module, etc.; the long sides of the fins of the two-phase assembly modules are arranged in the vertical direction or nearly vertical direction in the horizontal air duct; the horizontal cross-section of the dehumidifier two-phase assembly perpendicular to the long sides of the fins is a sawtooth-shaped zigzag. The ultra-high energy efficiency dehumidifier includes a shell, the above-mentioned dehumidifier two-phase assembly, a compressor, and an exhaust chamber; the air outlet on the back panel corresponds to the air intake of the vertically arranged fan; the exhaust port of the exhaust chamber is located on the side plate or back plate of the shell. This invention taps into the potential of the low-temperature exhaust "cold" resources of the evaporator, implements deep subcooling of the condensate for efficient dehumidification; and constructs a heavy-duty two-phase assembly to achieve ultra-high energy efficiency dehumidification.

Description

Technical Field

[0001] This invention belongs to the field of new energy technology, and in particular relates to a dehumidifier assembly with two heat exchangers and its ultra-high energy efficiency dehumidifier. 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 high-efficiency heat exchanger structure for dehumidifiers, including a condenser and an evaporator; characterized in that: the condenser includes a main condenser and a subcooled condenser; the evaporator, subcooled condenser, and main condenser are arranged sequentially along the airflow direction; the condenser and evaporator are arranged at different heights, and the air inlet above the evaporator is connected to the subcooled air inlet at the top of the subcooled condenser. Existing technology also discloses an industrial mobile dehumidifier with upward airflow using a parallel-flow condenser, including a housing assembly, a dehumidification system assembly, an axial fan assembly, a liquid level control device, a water storage tank, and an electrical control device. The dehumidification system consists of a compressor, a liquid receiver, a capillary tube, a filter, a solenoid valve, a parallel-flow condenser, and an evaporator; however, this technology has relatively low dehumidification efficiency and load intensity.

[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 problems in the prior art, this invention provides a dehumidifier assembly consisting of two separate units;

[0008] Another objective of this invention is to provide an ultra-high energy efficiency dehumidifier with a dehumidifier assembly.

[0009] To solve the above-mentioned technical problems, the technical solution of the present invention is as follows:

[0010] A dehumidifier dual-unit assembly, comprising: a dual-unit combination module; or a horizontal cross-section V-shaped dual-unit combination module composed of at least two dual-unit combination modules; or a structure composed of a dual-unit combination module and the horizontal cross-section V-shaped dual-unit combination module; or a structure composed of one or more of the dual-unit combination module and the horizontal cross-section V-shaped dual-unit combination module, and 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 a horizontal air duct; the horizontal cross-section of the dehumidifier dual-unit assembly perpendicular to the long side of the fins is a sawtooth-shaped zigzag.

[0011] 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, condensing section, subcooling section, and evaporator are flat plate finned tube heat exchangers and / or microchannel heat exchangers.

[0012] Furthermore, the horizontal cross-section of the dehumidifier assembly perpendicular to the long side of the fin is V-shaped, N-shaped, or a sawtooth shape formed by continuously arranging at least two V-shaped two-unit combination modules perpendicular to the long side of the fin.

[0013] 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°.

[0014] Preferably, the apex angle α of the horizontal cross-section V-shaped two-element combination module is 30° to 90°.

[0015] Preferably, the apex angle α of the horizontal cross-section V-shaped two-electrode combination module is 30° to 60°.

[0016] Furthermore, one side of the cross-section of the dehumidifier assembly perpendicular to the long side of the fins is the air inlet side of the heat exchanger, and the other side is the air outlet side of the heat exchanger.

[0017] 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°.

[0018] The incoming airflow impacts the tip of each fin in the flat-plate finned tube heat exchanger at an obtuse angle β, is reflected by the fins, enters the fin gap, passes through the combined module of the two heat exchangers, and flows into the negative pressure chamber.

[0019] 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.

[0020] δ=d·sinα / 2, where α is the apex angle of the horizontal cross-section V-shaped two-electrode combination module;

[0021] 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°.

[0022] Evaporators and condensers include fins and heat exchange tubes; multiple parallel fins spaced at a certain distance form a fin group; heat exchange tubes are installed in a direction perpendicular to the plane of the fins.

[0023] Along the short side of the fins, groups of heat exchange tubes are arranged in parallel and side by side, passing through the fins.

[0024] The heat exchange tubes in the heat exchange tube assembly are arranged along the long side of the fins.

[0025] Heat exchange tubes are refrigerant pipes or refrigerant sub-pipes.

[0026] Furthermore, the evaporator, subcooling section, condensing section, and superheating section are arranged adjacent to each other. The evaporator is embedded in the condenser; the superheating section is located above the evaporator, subcooling section, and / or condensing section arranged side by side; the subcooling section is disposed between the condensing section and the evaporator.

[0027] 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, and 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.

[0028] As a preferred embodiment, 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.

[0029] 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.

[0030] 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.

[0031] 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.

[0032] A high-efficiency dehumidifier includes a housing, a dehumidifier assembly, a compressor, a negative pressure chamber, and an exhaust chamber. The negative pressure chamber is composed of the dehumidifier assembly, part of the housing, and a back plate. The back plate is provided with a plurality of air outlets for the negative pressure chamber, and each air outlet is provided with a vertically arranged fan.

[0033] 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;

[0034] 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.

[0035] As a preferred embodiment, the ultra-high energy efficiency dehumidifier is equipped with two sets of dehumidifier assemblies, two compressors, and an exhaust chamber; the two sets of dehumidifier assemblies are arranged vertically and form two independent negative pressure chambers.

[0036] Furthermore, the back plate of the negative pressure chamber 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 flow fan; more preferably, the centrifugal fan is a backward-inclined external rotor centrifugal fan.

[0037] 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.

[0038] 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.

[0039] 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.

[0040] Furthermore, a compressor chamber for housing a compressor and an electrical box is provided on the outer side of the exhaust cavity back plate, or on the outer side of the negative pressure cavity, or below the exhaust cavity and / or negative pressure cavity.

[0041] Furthermore, a water tank for collecting condensate is provided below the exhaust chamber and / or negative pressure chamber.

[0042] Compared with the prior art, the present invention has the following beneficial effects:

[0043] ① Explore the potential of the low-temperature outlet air of the evaporator and implement deep subcooling of condensate for efficient dehumidification.

[0044] The ultra-high efficiency dehumidifier of this invention splits the condenser into three sections connected in series, 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 unlocks the potential of the "cold" resource of the dehumidifier's evaporator after "dehumidification" by directing the cold air outlet of the evaporator directly towards the end of the condenser, which is responsible for the subcooling heat release of the condensate. Furthermore, it cuts off the fin thermal bridge between the end of the condenser, which is responsible for the subcooling heat release, and the middle section of the condenser, which is responsible for the condensation heat release. This blocks the heat transfer from the high-temperature condensation section to the subcooled section at the end of the condenser, fully utilizing the "cold source" effect of the low-temperature air outlet after dehumidification. This significantly increases the subcooling degree of the refrigerant at the end of the condenser, thereby significantly reducing the refrigerant dryness at the throttle valve outlet and the evaporator inlet, and significantly increasing the evaporator's cooling capacity, achieving deep subcooling and high-efficiency dehumidification.

[0045] 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 proportion 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 proportion to around 0.85. The evaporator's cooling and dehumidification capacity is not simply increased by (0.85-0.65)×100%=20%, but rather by using the previous traditional dehumidifier's "0.65" as a base for comparison. By employing "deep subcooling" technology, the dehumidifier's evaporator's cooling and dehumidification capacity are significantly increased by (0.85-0.65) / 0.65×100%=30.77%.

[0046] ② A heavy-duty dual-unit assembly was constructed, achieving ultra-high energy efficiency dehumidification.

[0047] 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.

[0048] This invention utilizes at least two vertically mounted centrifugal fans on a wall to draw air from the negative pressure chamber of the dehumidifier's two-phase assembly, creating a negative pressure within the chamber. This negative pressure draws indoor ambient air, currently at 0 Pa static pressure (gauge pressure), into the main unit at a medium speed (approximately 4 m / s). The airflow is dispersed and slowed by a multi-fin planer blade that progressively cuts through the airflow. It then flows at a low speed (below 2 m / s) through the gaps between the fins of the dehumidifier's two-phase assembly to exchange heat. Afterward, it enters the negative pressure chamber, where it converges and accelerates, flowing at high speed into the centrifugal fan intake, where the pressure is lowest (gauge pressure is negative), completing the first static-to-dynamic pressure conversion. The high-speed airflow into the centrifugal fan intake is then 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 at high speed (approximately 8 m / s) into the indoor ambient air through a small exhaust port for diffusion and dilution.

[0049] 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 air inlet section before the dehumidifier's two-phase assembly and the air 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 results in a heavy-duty two-phase assembly that achieves ultra-high energy efficiency dehumidification.

[0050] In this invention, flow 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

[0051] Figure 1 Example 1 uses a pressure-enthalpy diagram of refrigerant circulation analysis to reduce the refrigerant vaporization ratio in the throttle valve by increasing the refrigerant subcooling at the condenser terminal, thereby increasing the refrigerant evaporation ratio in the evaporator and improving the cooling and dehumidification capacity.

[0052] Figure 2This is a structural diagram of the two-phase system in Example 1, which improves the subcooling of the refrigerant at the end of the condenser to reduce the refrigerant vaporization ratio at the throttle valve, increase the evaporator's cooling capacity, and improve the dehumidification efficiency.

[0053] Figure 3 This is a structural diagram of the sawtooth-shaped dehumidifier assembly in Example 1, which improves the subcooling of the refrigerant at the end of the dehumidifier condenser to reduce the refrigerant vaporization ratio of the throttling valve, increase the cooling capacity of the evaporator, and improve the dehumidification efficiency.

[0054] Figure 4 This is a three-dimensional view of the ultra-high energy efficiency dehumidifier in Example 1;

[0055] Figure 5 This is a top view of the structure of the ultra-high energy efficiency dehumidifier in Example 1;

[0056] Figure 6 This is a top view of the airflow during operation of the two-unit assembly of the ultra-high energy efficiency dehumidifier in Example 1;

[0057] Figure 7 Example 1 uses a front-mounted fan wall with a small exhaust vent and a rear-mounted dehumidifier assembly. During operation, the "fin planer" at the fin gap inlet of the dehumidifier scales the incoming airflow in stages, causing it to slow down and pass through the fin gap. (Horizontal cross-sectional view)

[0058] Figure 8 This is a vertical sectional view of the upper and lower structure of the sawtooth-shaped dehumidifier assembly in Example 2.

[0059] Figure 9 This is a horizontal sectional view of the upper and lower structures of the sawtooth-shaped dehumidifier assembly in Example 2, consisting of dehumidifiers AA and BB.

[0060] Figure 10 This is a top view of the dehumidification airflow operation of the two-unit dehumidifier assembly in Example 2, which uses a sawtooth-shaped zigzag dehumidifier.

[0061] Figure 11 This is a vertical cross-sectional view of the airflow operation of the two-unit assembly of the sawtooth-shaped dehumidifier with top air outlet, as shown in Example 3.

[0062] Figure 12 This is a vertical sectional view of the dual-duct composite dehumidification system with two dehumidification units installed inside the housing in Example 4.

[0063] Figure 13 This is a horizontal sectional view of the dual-duct composite dehumidification system with two dehumidification units installed inside the housing in Example 4.

[0064] Figure 14 This is a vertical sectional view of the airflow operation of the dual-duct composite dehumidification system with two dehumidification units installed inside the housing in Example 4.

[0065] Figure 15 This is a diagram of the fin structure of a dehumidifier single-duct composite system in Example 5, where the subcooling section, condensing section, and superheating heat release section of the condenser and the evaporator of two adjacent sets of two-unit assemblies are connected by longitudinal and transverse thermal bridges.

[0066] Figure 16 for Figure 15 A magnified view of a section at point A in the middle;

[0067] Figure 17 This is a structural diagram of the end plate of the single-duct dehumidifier composite system in Example 5, where the subcooling section, condensing section, and superheating heat release section of the condenser and the evaporator of the two adjacent sets of two-unit assemblies are connected by longitudinal and transverse thermal bridges of the fins, respectively.

[0068] Figure 18 This is a vertical sectional view of the airflow operation of a single-duct composite dehumidification system with two dehumidification units installed inside the housing, as shown in Example 5.

[0069] Figure 19 This is a top view of the fan wall-mounted dehumidifier structure using a three-finned tube assembly as described in Example 6.

[0070] Figure 20 This is a top view of the airflow during operation of the front-mounted dehumidifier using a three-finned tube assembly in Example 6. Detailed Implementation

[0071] 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.

[0072] 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.

[0073] 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.

[0074] 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.

[0075] Example 1

[0076] like Figure 1-7 As shown, a dehumidifier two-unit assembly is provided. The dehumidifier two-unit assembly 2 is a horizontal cross-section V-shaped two-unit combination module 22 composed of two two-unit combination modules 21. The long side of the fins 23 of the two-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 two-unit assembly 2 perpendicular to the long side of the fins is a sawtooth-shaped zigzag line.

[0077] The two-unit combination module 2 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.

[0078] The horizontal cross-section of the dehumidifier assembly 2, which is perpendicular to the long side of the fins 23, is V-shaped.

[0079] The apex angle α of the horizontal cross-section V-shaped two-electrode combination module 22 is 15° to 110°.

[0080] As a preferred embodiment, the apex angle α of the horizontal cross-section V-shaped two-electrode combination module 22 is 30° to 90°.

[0081] As a preferred embodiment, the apex angle α of the horizontal cross-section V-shaped two-electrode combination module 22 is 30° to 60°.

[0082] The heat exchanger air inlet side of the cross section of the dehumidifier two-phase assembly 2 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 two-phase assembly), and the other side is the air outlet side of the heat exchanger (i.e., the air outlet side of the dehumidifier two-phase assembly).

[0083] 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°.

[0084] The incoming airflow impacts the tip of each fin in the flat-plate finned tube heat exchanger at an obtuse angle β, is reflected by the fins, enters the fin gap, passes through the combined module of the two heat exchangers, and flows into the negative pressure chamber.

[0085] 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.

[0086] δ=d·sinα / 2, where α is the apex angle of the horizontal cross-section V-shaped two-electrode combination module 22;

[0087] 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 being 39° and the incident obtuse angle β being 109.5°.

[0088] 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.

[0089] 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.

[0090] The heat exchange tubes 29 in the heat exchange tube assembly 291 are arranged along the long side of the fins 23.

[0091] Heat exchange tube 29 and heat exchange tube assembly 291 are equivalent to refrigerant piping or refrigerant sub-pipes.

[0092] Evaporator 28, subcooling section 27, condensing section 26 and superheating section 25 are arranged adjacent to each other, with evaporator 28 embedded in condenser 24; superheating section 25 is located above evaporator 28, subcooling section 27 and condensing section 26 arranged side by side; subcooling section 27 is located between condensing section 26 and evaporator 28.

[0093] The refrigerant lines of the superheated heat release section 25, the condensing section 26, and the subcooling section 27 are connected in series; the output end of the subcooling section 27 of the condenser 24 is connected to the input end of the evaporator 28 through a throttling device.

[0094] The refrigerant piping of the evaporator 28 includes four parallel refrigerant sub-pipes. The refrigerant piping outlet of the subcooling section 27 is connected to the inlet of the four refrigerant sub-pipes respectively through a throttling device.

[0095] The refrigerant piping of the superheated heat release section 25 includes two parallel refrigerant sub-pipes, which are arranged vertically.

[0096] 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;

[0097] 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.

[0098] Finned thermal bridges are provided between heat exchange tube groups in the superheating and heat dissipation section, between heat exchange tube groups in the condensing section, between heat exchange tube groups in the subcooling section, and between heat exchange tube groups in the evaporator.

[0099] A high-efficiency dehumidifier includes a housing 1, a dehumidifier assembly 2, a compressor 3, and an exhaust chamber 4; the negative pressure chamber 5 is composed of the housing 1 including the dehumidifier assembly 2, a portion of the housing 1, and a back plate 51; the back plate 51 is provided with two air outlets 52 of the negative pressure chamber 5, and the air outlets 52 are provided with vertically arranged fans 6.

[0100] The dehumidifier assembly 2 is located on the air inlet surface 11 of the housing 1, and the dehumidifier assembly 2 is the air inlet of the negative pressure chamber 5;

[0101] The air outlet 52 on the back plate 51 corresponds to the air intake of the vertically arranged fan 6; the air outlet 52 is connected 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.

[0102] Each air outlet of the back panel 51 is equipped with a fan 6, forming a fan wall; the fan 6 is a backward-inclined external rotor centrifugal fan.

[0103] 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.

[0104] The exhaust surface enclosed by the exhaust port 41 is located on the top plate 13 of the housing, and the air inlet surface 11 is located on the front of the housing 1.

[0105] The outer side of the negative pressure chamber 5 is provided with a compressor chamber 31 for housing the compressor 3 and the electrical box.

[0106] As a preferred implementation, the ultra-high efficiency dehumidifier can be fixedly installed, and the drain outlet of the evaporator drip tray can be directly connected to the sewer to discharge the condensate generated during dehumidification. For example... Figure 1-7As shown in the figure, this embodiment analyzes the operation of dehumidifiers in indoor spaces such as basements, warehouses, workshops, and residences. The dehumidifier operates in an indoor environment where, apart from a slightly high humidity level, the 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, where 26.7°C is converted from 80°F), which confirms the typical operating environment of the dehumidifier. Under the standard condition of 27°C 60%, the physical properties of the air, such as density, enthalpy, and viscosity, are relatively moderate, which is conducive to significantly improving the dehumidifier's dehumidification efficiency to above 3.5L H2O / kwh. It is also conducive to significantly increasing the dehumidifier's cooling load intensity, reducing the main unit volume occupied by each 1L H2O / h dehumidification capacity to below 50L.

[0107] This embodiment aims to improve the dehumidification energy efficiency ratio and cooling load intensity of the dehumidifier. Starting from the physics and thermodynamics, it reorganizes the dehumidifier's two-phase system and refrigerant circuit, reorganizes the two-phase system and air circuit, recouples the refrigerant circuit and air circuit, and reconstructs the dehumidifier.

[0108] ① The dehumidifier product design closely adheres to the core concept of "reducing the dryness of the two-phase refrigerant at the outlet of the expansion valve".

[0109] 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.

[0110] The refrigerant dryness fraction at the evaporator inlet refers to the proportion of gaseous refrigerant 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.

[0111] The refrigerant "dryness" at the outlet of the expansion valve and 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 at the outlet of the condenser and the inlet of the expansion valve to the saturation temperature corresponding to the low-pressure state at the outlet of the expansion valve and the inlet of the evaporator, a portion of the liquid refrigerant vaporizes and absorbs heat in the expansion valve 222, causing the other portion of the liquid refrigerant to cool down. As a result, the refrigerant injected into the inlet of the evaporator is not a liquid refrigerant with a dryness of 0, but a gas-liquid two-phase flow with a dryness of x. The dryness of x can be 0.2 (liquid ratio 0.8), 0.3 (liquid ratio 0.7), 0.4 (liquid ratio 0.6), or even 0.5 (liquid ratio 0.5).

[0112] The refrigerant dryness fraction (x) at the outlet of the throttling valve and the inlet of the evaporator in a dehumidifier is determined by the "subcooling" of the refrigerant at the end of the condenser. If the condensate at the end of the condenser releases heat sufficiently and has a low temperature, meaning the "subcooling" of the condensate is high, it will enter the evaporator through the throttling valve 222. Since the temperature difference between the condensate at the end of the condenser and the evaporation temperature is small, and the heat release is small, the proportion of refrigerant undergoing a "phase change" and absorbing heat through vaporization in the throttling valve is relatively low. Consequently, the refrigerant dryness fraction (x) at the outlet of the throttling valve and the inlet of the evaporator is correspondingly low, sometimes as low as 0.2 or even below. A higher refrigerant dryness fraction (x) results in a larger cooling capacity. Conversely, if the condensate at the condenser terminal does not release heat sufficiently and has a high temperature (i.e., the condensate has low subcooling), the temperature difference between the condensate at the condenser terminal and the evaporation temperature is large, resulting in a large amount of heat release. Consequently, a relatively high proportion of the condensate undergoes a phase change and vaporizes to absorb heat when passing through the condenser. This leads to a correspondingly higher refrigerant dryness fraction (x) at the condenser outlet and evaporator inlet, reaching 0.3 or even above 0.4. Consequently, the proportion of the refrigerant liquid phase entering the evaporator is relatively low, resulting in a smaller evaporator cooling capacity.

[0113] Therefore, the ultra-high energy efficiency dehumidifier in 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.

[0114] ② Innovative Structure of Ultra-High Energy Efficiency Dehumidifier

[0115] The ultra-high energy efficiency dehumidifier in this embodiment starts from the refrigeration cycle of the refrigerant pressure-enthalpy diagram and uses a high-efficiency evaporator-condenser sub-module to construct the dehumidifier assembly.

[0116] The high-efficiency dehumidifier evaporator-condenser submodule used in the dehumidifier assembly of this embodiment 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.

[0117] This ultra-high efficiency dehumidifier, based on the principle that "increasing the subcooling of the refrigerant at the end of the condenser reduces the proportion of refrigerant vaporization in the expansion valve, thereby increasing the proportion of refrigerant evaporation in the evaporator and increasing the cooling and dehumidification capacity," uses a parallel arrangement of the evaporator and condenser. The condenser is divided into three sections connected in series, 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 leverages the potential of the dehumidifier's evaporator to deliver low-temperature air after dehumidification, thus increasing the cooling and dehumidification capacity. The evaporator's cold air outlet is directly facing the end of the condenser, which is responsible for the subcooling and heat release of the condensate. It also cuts off the thermal bridge between the end of the condenser, which is responsible for the subcooling and heat release, and the middle section of the condenser, which is responsible for the condensing and heat release. This blocks the conduction of heat from the high-temperature condensing section to the subcooled section at the end of the condenser, fully utilizing the "cold source" effect of the low-temperature air outlet after the evaporator dehumidifies. This significantly increases the subcooling degree of the refrigerant at the end of the condenser, thereby significantly reducing the refrigerant dryness at the outlet of the expansion valve and the inlet of the evaporator, significantly increasing the evaporator's cooling capacity, and implementing deep subcooling and efficient dehumidification.

[0118] The ultra-high energy efficiency dehumidifier in this embodiment uses a high-efficiency evaporator-condenser sub-module to construct a dehumidifier two-unit assembly: two high-efficiency evaporator-condenser two-unit combination modules are combined to form a horizontal cross-section V-shaped dehumidifier two-unit assembly (i.e., dehumidifier two-unit assembly); the horizontal cross-section of the dehumidifier two-unit assembly perpendicular to the long side of the fins is a sawtooth-shaped broken line.

[0119] In this embodiment, within the limited space of the dehumidifier, a horizontal cross-section V-shaped two-phase assembly module is set parallel to the air inlet surface of the dehumidifier main unit. A large-area ventilation surface for the high-efficiency evaporator-condenser sub-modules is obtained by unfolding the module along its air inlet surface. A second unfolding on this ventilation surface further creates a large-area finned heat transfer surface, thereby effectively increasing the total finned heat transfer area of ​​the dehumidifier's two-phase assembly, reducing the temperature difference between the evaporator and condenser bodies, increasing evaporation pressure, reducing condensation pressure, and improving the cooling capacity and energy efficiency ratio of the dehumidifier's refrigeration system.

[0120] This embodiment of the ultra-high energy efficiency dehumidifier features a single negative pressure chamber, which is composed of a base plate, side plates, a back plate, a dehumidifier assembly, and a top plate. The back plate has a horizontally continuous V-shaped two-unit assembly module with upper and lower negative pressure chamber outlets. A backward-curved external rotor centrifugal fan is installed at each of these outlets, serving as the fan's intake. The back plate, with its negative pressure chamber outlets and the rear-curved external rotor centrifugal fan wall, forms the fan wall. An exhaust chamber is located outside the fan wall, consisting of the back plate (fan wall), side plates, upper and lower bottom surfaces, and an outer surface. The exhaust outlet is located on the top surface of the exhaust chamber. A compressor chamber is located on the side of the assembly, housing the dehumidifier compressor, four-way valve, expansion valve, electrical box, and other refrigerant circuit components.

[0121] ③ Innovative design of the inlet and outlet airflow of the dehumidifier's two-phase assembly

[0122] During the ventilation and heat exchange operation of the two-unit assembly of the ultra-high efficiency dehumidifier in this embodiment, the airflow from the main unit's air inlet to the air outlet is powered by a centrifugal fan. The heat exchange airflow undergoes two static pressure-dynamic pressure conversions. The first static pressure-dynamic pressure conversion enables high-speed airflow to be drawn into the centrifugal fan's air inlet, and the second static pressure-dynamic pressure conversion enables high-speed airflow to be discharged from the exhaust outlet of the exhaust chamber. 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 in this embodiment.

[0123] In this embodiment, two centrifugal fans on the fan wall establish the airflow field for the dehumidifier assembly: the two vertically positioned centrifugal fans draw air from the negative pressure chamber of the dehumidifier assembly, creating negative pressure within the chamber. This 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 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, where the pressure is lowest (gauge pressure is negative), completing the first static-dynamic pressure conversion. The high-speed airflow into the centrifugal fan intake 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) through a 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 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.

[0124] 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 two-device assembly.

[0125] 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.

[0126] 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.

[0127] 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.

[0128] In this embodiment, a compressor chamber is set outside the dehumidifier's two-phase assembly, housing 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. These refrigeration circuit components, along with the two-phase assembly, refrigerant connecting pipes, and other components, form the dehumidifier's refrigeration cycle circuit in the order of compressor-condenser-expansion valve-evaporator-compressor. The compressor serves as the power source for the refrigeration cycle circuit, establishing 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." Specifically, the refrigerant liquid absorbs heat through evaporation in the evaporator pipes and then absorbs heat from the ambient air flowing between the fins through the large heat-absorbing area of ​​the copper tubes, thus achieving "cooling and dehumidification." Then, the high-temperature, high-pressure refrigerant gas condenses and releases heat in the condenser pipes and releases heat to the ambient air flowing between the fins through the large heat-releasing area of ​​the copper tubes, achieving the migration of heat from the air being cooled and dehumidified by the dehumidifier's evaporator to the "reheated" air after dehumidification by the condenser.

[0129] Example 2

[0130] like Figure 8-10As shown, both this embodiment and Embodiment 1 use a sawtooth-shaped dehumidifier assembly. When the dehumidifier is running, it takes advantage of the technology of the fin planer blades to plan the airflow in stages to slow down the airflow and distribute it through the gap between the fins, thereby improving the load intensity and energy efficiency ratio of the dehumidifier.

[0131] The difference in this embodiment is that it adopts an upper and lower structure, combining the sawtooth-shaped dehumidifier assembly 2 with the compressor cavity 31 to form an ultra-high energy efficiency dehumidifier with an upper and lower structure.

[0132] Below the exhaust chamber 4 and the negative pressure chamber 5, there is a compressor chamber 31 for housing the compressor 3 and the electrical box.

[0133] A water tank 32 for collecting condensate is installed below the exhaust chamber 4 and the negative pressure chamber 5.

[0134] The exhaust chamber 4 is composed of a side plate of the housing, a top plate, a back plate of the negative pressure chamber, and an exhaust chamber back plate.

[0135] The exhaust surface enclosed by the exhaust vent 41 is set on the back plate of the exhaust cavity.

[0136] In this embodiment, when the axial fan is running, the airflow is driven to flow through the sawtooth-shaped dehumidifier assembly 2. The main body of the airflow first flows through the evaporator 28, where it is cooled and dehumidified. After the moisture is filtered out, it flows through the condenser 24 to achieve "reheating" and then is discharged from the dehumidifier.

[0137] This embodiment has all the advantages of embodiment 1. The dehumidifier in this embodiment can be fixedly installed and the drain outlet 281 of the evaporator water tray can be directly connected to the sewer to discharge the condensate generated during dehumidification.

[0138] In this embodiment, a water tank 32 can also be installed in the compressor cavity 31 to collect the condensate from the two dehumidifier assemblies above, thus becoming a household portable dehumidifier with universal applicability.

[0139] Example 3

[0140] like Figure 11 As shown, the principle and structure of this embodiment are basically the same as those of Embodiment 2.

[0141] The difference in this embodiment is that the fan 6 is a backward-inclined external rotor centrifugal fan.

[0142] This embodiment uses a backward-inclined external rotor centrifugal fan, which provides stronger airflow. The top-discharge exhaust method is beneficial for organizing airflow circulation within the space to be dehumidified, and reduces the floor space occupied by the exhaust area in scenarios using axial flow fans, further improving space utilization.

[0143] Example 4

[0144] like Figure 12-14 As shown, this embodiment is basically the same as the principle and structure of embodiment 2. The two-unit assembly 2 of the dehumidifier adopts a horizontal cross-section sawtooth-shaped broken line structure, and the fan 6 adopts a backward-inclined external rotor centrifugal fan.

[0145] The difference in this embodiment is that the ultra-high energy efficiency dehumidifier is equipped with two sets of dehumidifier assemblies 2, two compressors 3, and an exhaust chamber 4; the two sets of dehumidifier assemblies 2 are arranged vertically and form two independent negative pressure chambers 5.

[0146] This embodiment is a composite system. Two dehumidification units are installed inside the housing 1. The compressors 3 of the two dehumidification units are both located in the compressor chamber 31 at the bottom. The two dehumidifier assemblies 2 are stacked vertically with their air inlets on the same side and in the same direction. The two fans 6 are staggered vertically and horizontally to form two exhaust chambers 4. The two fans 6 and the two dehumidifier assemblies 2 are combined to form two independent air ducts.

[0147] In this embodiment, the spatial structure relationship between the two-unit dehumidifier assembly 2, the fan 6, and the inlet and outlet air ducts is further optimized by setting two sets of refrigeration and dehumidification units inside the casing. This significantly improves the load intensity of the composite dehumidifier system. Under the standard operating conditions of 27℃ and 60%, the dehumidification energy efficiency not only reaches more than 3.5L / kwh, but also the energy density (load intensity) reaches less than 50L of the main unit volume occupied by every 1L H2O / h dehumidification capacity, which has the characteristics of "overload".

[0148] Example 5

[0149] like Figure 15-18 As shown, in this embodiment, both the dehumidifier assemblies 2 and 6 adopt a horizontal cross-section sawtooth-shaped broken line structure, and both adopt a backward-inclined external rotor centrifugal fan.

[0150] A dehumidifier two-phase assembly differs from the dehumidifier two-phase assembly 2 of Embodiment 1 in that: the dehumidifier two-phase assembly 2 is a horizontal cross-section V-shaped two-phase assembly module 22 consisting of two two-phase assembly modules 21; the two-phase assembly module 21 is provided with two sets of condensers 24 and two sets of evaporators 28.

[0151] The two condensers and two evaporators in the two-unit combination module belong to two independent refrigeration and dehumidification systems.

[0152] Two sets of condensers 24 and two sets of evaporators 28 are set on the same fin assembly; on the fins 23, longitudinal and transverse gaps 221 are provided between the superheated heat release section 25, the condensing section 26, the subcooling section 27 and the evaporator 28 in the two-electrode combination module 21 to cut off the thermal bridge of the fins and longitudinal and / or transverse fin ribs to fix the relative spatial structural relationship of each region of the fins.

[0153] 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.

[0154] The ultra-high efficiency dehumidifier in this embodiment is similar to that in embodiment 4, both being composite systems. The difference lies in that: two dehumidification units are installed inside the housing 1; the compressors 3 of both dehumidification units are located in the compressor chamber 31 at the bottom. The superheated heat release section 25, condensing section 26, subcooling section 27, and evaporator 28 of the two dehumidifier assemblies are arranged adjacent to each other on the same fin assembly. Longitudinal and transverse gaps for cutting off thermal bridges between the superheated heat release section 25, condensing section 26, subcooling section 27, and evaporator 28 of the two adjacent dehumidifier assemblies 2 are provided, as well as fin ribs for fixing the relative spatial structural relationship of each region of the fins.

[0155] This embodiment, by incorporating two sets of refrigeration and dehumidification units within the casing, further optimizes the spatial structure of the dehumidifier assembly, fan, and inlet / outlet ducts. Specifically, the longitudinal and transverse gaps 221 between the condenser superheating section, condensing section, subcooling section, and evaporator of the two adjacent dehumidifier assemblies, used to cut off fin thermal bridges, and the fin ribs used to fix the relative spatial structure of each fin region, allow each heat exchanger assembly to utilize the fin area of ​​the corresponding heat exchanger adjacent to the other, non-operating refrigeration and dehumidification unit when operating independently. This effectively expands the fin heat exchange area, increases evaporation temperature and pressure, reduces condensation temperature and pressure, and improves the dehumidification efficiency ratio. Under standard operating conditions of 27℃ and 60%, the dehumidification efficiency reaches over 3.5L / kWh, exhibiting "ultra-high efficiency."

[0156] Example 6

[0157] like Figures 19-20 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 4 are arranged in a linear progression, and the compressor chamber 31 is placed on the side.

[0158] The difference in this embodiment is that the dehumidifier assembly 2 is composed of three two-unit combination modules 21; among them, two two-unit combination modules 21 form a horizontal cross-section V-shaped two-unit combination module 22. Another flat two-unit combination module is independently set outside the horizontal cross-section V-shaped two-unit combination module 22, and a partition 223 perpendicular to the air inlet surface is set 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 5 of the two-unit combination module.

[0159] 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 compared to a single horizontal cross-section V-shaped two-phase combination module 22, thus meeting the needs of dehumidifiers with larger cooling and dehumidification capacities.

[0160] 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 high-efficiency dehumidifier, characterized in that, It includes a housing, a dehumidifier assembly, a compressor, a negative pressure chamber, and an exhaust chamber; the negative pressure chamber is composed of the dehumidifier assembly, upper and lower base plates, left and right side plates, and a back plate; the back plate is provided with several air outlets for 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 dehumidifier assembly is a horizontal cross-section V-shaped two-unit combination module composed of at least two two-unit combination modules; or a structure composed of two-unit combination modules and the horizontal cross-section V-shaped two-unit combination module; or a structure composed of one or two of the two-unit combination modules and the horizontal cross-section V-shaped two-unit combination module, and 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 dehumidifier assembly perpendicular to the long side of the fins is a sawtooth-shaped zigzag. The two-unit 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 flat plate finned tube heat exchangers. 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 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 incoming airflow impacts the tip of each fin in the flat plate finned tube heat exchanger at an obtuse angle β, is reflected by the fins, enters the fin gap, passes through the two-unit combined module, 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-electrode combination module.

2. The ultra-high energy efficiency dehumidifier 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 a sawtooth shape formed by continuously arranging at least two V-shaped two-unit combination modules perpendicular to the long side of the fins.

3. The ultra-high energy efficiency dehumidifier according to claim 2, 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.

4. The ultra-high energy efficiency dehumidifier according to claim 2, characterized in that, The apex angle α of the horizontal cross-section V-shaped two-electrode combination module is 15° to 110°.

5. The ultra-high energy efficiency dehumidifier according to claim 1, characterized in that, 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.

6. The ultra-high energy efficiency dehumidifier according to claim 1, 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 module with horizontal cross-section.

7. The ultra-high energy efficiency dehumidifier according to claim 1, characterized in that, The evaporator, subcooling section, condensing section, and superheating section are arranged adjacent to each other, with the evaporator embedded in the condenser; the superheating section is located above the evaporator, subcooling section, and / or condensing section arranged side by side; the subcooling section is located between the condensing section and the evaporator.

8. The ultra-high energy efficiency dehumidifier 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.

9. The ultra-high energy efficiency dehumidifier 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.

10. The ultra-high energy efficiency dehumidifier according to claim 9, characterized in that, Two condensers and two evaporators are mounted on the same fin assembly; 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; 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.

11. The ultra-high energy efficiency dehumidifier according to claim 9, characterized in that, Each independent refrigeration and dehumidification system consists of a superheating section, a condensing section, a subcooling section, and an evaporator, each composed of multiple refrigerant piping branches connected in parallel, with each heat exchanger tube group of each refrigerant piping branch arranged side by side.

12. The ultra-high energy efficiency dehumidifier according to claim 11, characterized in that, The heat exchange tube bundles are arranged alternately side by side.

13. The ultra-high energy efficiency dehumidifier according to claim 1, characterized in that, The ultra-high energy efficiency dehumidifier is equipped with two sets of dehumidifier assemblies, two compressors, and an exhaust chamber; the two sets of dehumidifier assemblies are arranged vertically and form two independent negative pressure chambers.

14. The ultra-high energy efficiency dehumidifier according to claim 1, characterized in that, The back panel of the negative pressure chamber is equipped with at least two air outlets; each air outlet is equipped with a fan, forming a fan wall.

15. The ultra-high energy efficiency dehumidifier according to claim 14, characterized in that, The fan is either a centrifugal fan or an axial flow fan.

16. The ultra-high energy 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.

17. The ultra-high energy efficiency dehumidifier according to claim 16, characterized in that, The exhaust port of the exhaust chamber is a rectangular exhaust port.

18. The ultra-high energy efficiency dehumidifier according to claim 16, 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.

19. The ultra-high energy efficiency dehumidifier according to claim 1, 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.

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

21. The ultra-high energy efficiency dehumidifier according to claim 1, characterized in that, The ultra-high energy efficiency dehumidifier is equipped with two sets of dehumidifier assemblies, two compressors, one negative pressure chamber, and one exhaust chamber.

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