Finned tube heat exchanger assembly, air conditioner main unit and equipment platform of air conditioner main unit

Abstract

The invention belongs to the technical field of green energy conservation, and discloses a finned tube heat exchanger assembly, an air conditioner main unit and an equipment platform of the air conditioner main unit. The finned tube heat exchanger assembly comprises a plurality of finned tube heat exchangers and a plurality of refrigerant branches; the liquid distributing and collecting lotus head and the gas collecting and distributing pipe are arranged on the same end plate of the same finned tube heat exchanger or the end plates of different finned tube heat exchangers; the adjacent finned tube heat exchangers are communicated with refrigerant branches through refrigerant gap bridge pipelines, and refrigerant liquid pipes, communicated with the liquid distributing and collecting lotus heads, of the adjacent refrigerant branches on the same finned tube heat exchanger are arranged adjacently. And the superheat heat exchange section, the phase change heat exchange section and the supercooling heat exchange section of any refrigerant pipeline between the gas collecting and distributing pipe and the liquid distributing and collecting lotus head are distributed on each flat plate type finned tube heat exchanger. The structure and the process of the finned tube heat exchanger assembly are simplified, and the supercooling degree of condensate when the finned tube heat exchanger is used as a condenser and the steam superheat degree when the finned tube heat exchanger is used as an evaporator are improved.

Description

Technical Field

[0001] The present invention belongs to the technical field of green energy saving, and in particular relates to a fin-tube heat exchanger assembly, an air-conditioning mainframe and an equipment platform thereof. Background Art

[0002] Prior art Patent applications such as an air conditioner mainframe with vertically arranged fans and its equipment platform (application number 202310972409.9), a serrated zigzag fin-tube heat exchanger assembly and its air conditioner mainframe and equipment platform (application number 202311012468.8), etc., proposed the concepts of wind path coupling and energy coupling between the air conditioner mainframe and the equipment platform facade decorative structure, and adopted explicit external heat exchanger inlet and outlet duct built-in technology for the air conditioner mainframe and zigzag fin-tube external heat exchanger fin planer to implement step-by-step planing and low-speed air distribution technology for the incoming air flow, which subversively reorganized the internal structure of the air conditioner mainframe and the structural relationship between the air conditioner mainframe and the equipment platform facade. It has outstanding substantial characteristics and significant progress, and creates conditions for integrating the air path structure of the air conditioner mainframe into the equipment platform blinds. However, in the application practice of the above-mentioned prior art, there are some important process and technical problems, mainly:

[0003] (I) The refrigerant distribution and collection structure is complex, and the risk points of refrigerant leakage increase

[0004] The M-shaped fin-tube heat exchanger assembly in the above patented technology is composed of two V-shaped fin-tube modules. If it is connected to the compressor nearby, three liquid distribution lotus heads and three gas distribution pipes are required to implement the secondary distribution of the refrigerant and the secondary collection after the heat exchange phase change. When designing the whole system, it is necessary to go back and solve the problem of the primary distribution and primary collection of the refrigerant between the three liquid distribution lotus heads and the three gas distribution pipes.

[0005] The secondary distribution and secondary recovery of refrigerants in the above-mentioned large refrigeration systems result in complex piping structures and manufacturing processes for refrigerant distribution and recovery, and increase the risk points of refrigerant leakage.

[0006] (ii) When used as a condenser, the outlet condensate is not sufficiently subcooled, and when used as an evaporator, the outlet steam is not sufficiently superheated.

[0007] Fin-tube heat exchangers for air conditioners are usually made of copper tubes expanded with aluminum alloy fins, thus becoming a good conductor of heat and a metal structure with a temperature balance trend characteristic.

[0008] When the fin-tube heat exchanger operates as a condenser, the heat of the high-temperature and high-pressure refrigerant gas in the tube at the head of each branch is released to the air through the copper tube and the fins outside the tube, and is also transferred to the condensate in the terminal pipes of each branch through the fin heat bridge; in particular, the pipe at the end (subcooling section) of each branch is connected to the inlet pipe of the high-temperature refrigerant gas of the next branch through the fins, and passively receives the heat conducted by the inlet pipe of the next branch, making it difficult to deeply implement the "subcooling operation" of the condensate; and the condensate at the outlet of the condenser is insufficiently "subcooled", which increases the "dryness" of the refrigerant at the outlet of the throttle valve and reduces the heat absorption of the condensate entering the evaporator;

[0009] Similarly, when the finned tube operates as an evaporator, the thermal bridge effect of the fins also reduces the "superheat" of the steam at the evaporator outlet, thereby reducing the heat absorption of the evaporator and the heat release of the condenser.

[0010] Now, the fundamental change in the application scenarios of air conditioner hosts calls for disruptive innovation in the structure of the air conditioner host and the spatial relationship between the air conditioner host and the equipment platform:

[0011] First, driven by the policy of "equipment platform area is not included in the building gross floor area", the independent equipment platform with good accessibility of the "all-in-one" air-conditioning host with one-to-many multi-connections has been effectively implemented, and the potential of multi-connections in reducing noise radiation range and simple and elegant indoor and outdoor decoration has been fully explored, replacing one-to-one room air conditioners (split air conditioners) and becoming the mainstream product in the air-conditioning market;

[0012] Secondly, the traditional multi-split air-conditioning host with axial fan side outlet is hung on the outer wall of the building to enter the interior of the equipment platform. The inlet and outlet air paths of the external heat exchanger face unprecedentedly stringent spatial constraints of the equipment platform with "floor below, ceiling above, wall behind, and shutters in front". The side-outlet air-conditioning host faces the shutters, which leads to increased exhaust static pressure, reduced air volume, and partial short-circuit reflux in the reduced air volume, resulting in serious attenuation of air-conditioning performance and other problems that need to be solved urgently. Summary of the invention

[0013] In order to solve the above-mentioned problems in the prior art, the present invention provides a fin-tube heat exchanger assembly.

[0014] Another object of the present invention is to provide an air conditioner host;

[0015] Another object of the present invention is to provide a device platform.

[0016] In order to solve the above technical problems, the technical solution of the present invention is as follows:

[0017] A fin-tube heat exchanger assembly includes a fin-tube heat exchanger, a liquid distribution lotus head and a gas distribution pipe;

[0018] The finned tube heat exchanger includes, but is not limited to, single-row tube, double-row tube, triple-row tube, quadruple-row tube, and quintuple-row tube finned tube heat exchangers; the finned tube heat exchanger includes a number of refrigerant branches; the liquid refrigerant interfaces of each refrigerant branch are connected to the liquid collecting lotus head, and the gaseous refrigerant interfaces are connected to the gas collecting and distributing pipe; the liquid collecting lotus head and the gas collecting and distributing pipe are arranged at the same side end plate of the finned tube heat exchanger; the refrigerant liquid pipes connecting the liquid collecting lotus head of two refrigerant branches are arranged adjacent to each other on the same set of fin plates of the same row of finned tube heat exchanger.

[0019] Further, two adjacent refrigerant branches form a refrigerant pipeline module unit, and the two refrigerant liquid pipes in the refrigerant pipeline module unit are arranged adjacent to each other on the same set of fin plates of the same row of finned tube heat exchanger; or, the two refrigerant liquid pipes of two adjacent refrigerant pipeline module units are arranged adjacent to each other on the same set of fin plates of the same row of finned tube heat exchanger.

[0020] Further, the refrigerant gas pipes connected to the gaseous refrigerant interfaces of two adjacent refrigerant pipeline module units are arranged adjacent to each other on the same set of fin plates of the same row of finned tube heat exchanger; or, the two refrigerant gas pipes of the refrigerant pipeline module unit are arranged adjacent to each other on the same set of fin plates of the same row of finned tube heat exchanger.

[0021] A finned tube heat exchanger assembly includes a number of flat-plate finned tube heat exchangers, one liquid collecting lotus head, and one gas collecting and distributing pipe; the flat-plate finned tube heat exchanger includes, but is not limited to, single-row tube, double-row tube, triple-row tube, quadruple-row tube, and quintuple-row tube finned tube heat exchangers; the flat-plate finned tube heat exchanger includes a number of refrigerant branches; the refrigerant branches between different flat-plate finned tube heat exchangers are connected in series through refrigerant crossover pipelines; the refrigerant branches are connected to the liquid collecting lotus head and the gas collecting and distributing pipe to form the finned tube heat exchanger assembly.

[0022] Further, the liquid collecting lotus head and the gas collecting and distributing pipe are arranged at the same side end plate of the same flat-plate finned tube heat exchanger; or are respectively arranged at the end plates of different flat-plate finned tube heat exchangers.

[0023] Further, the refrigerant branches between adjacent flat-plate finned tube heat exchangers are connected through refrigerant crossover pipelines to distribute the superheat heat exchange section, phase change heat exchange section, and subcooling heat exchange section of any refrigerant branch between the gas collecting and distributing pipe and the liquid collecting lotus head to each flat-plate finned tube heat exchanger; or, any refrigerant branch between the gas collecting and distributing pipe and the liquid collecting lotus head is segmented and arranged in each flat-plate finned tube heat exchanger.

[0024] Further, the refrigerant liquid pipes connecting the liquid collecting lotus head of two refrigerant branches are arranged adjacent to each other on the same set of fin plates of the same row of finned tube heat exchanger.

[0025] Further, the refrigerant gas pipes of the connecting header pipe of the two refrigerant branches are arranged far apart on the same set of fin plates of the same row of finned tube heat exchangers.

[0026] Further, the total lengths of the refrigerant pipelines of any refrigerant branch between the liquid distribution lotus head and the connecting header pipe are equal or substantially equal.

[0027] An air-conditioning main unit includes the finned tube heat exchanger assembly.

[0028] Further, the air-conditioning main unit includes a housing, a negative pressure chamber, an exhaust chamber, a compressor chamber, and a fan; the negative pressure chamber and the exhaust chamber are arranged side by side; the compressor chamber is arranged outside the first back plate of the negative pressure chamber and / or the exhaust chamber; the suction port direction of the fan is orthogonal or nearly orthogonal to the main air outlet direction of the finned tube heat exchanger assembly, constructing an air flow vortex chamber between the air outlet of the finned tube heat exchanger assembly in the negative pressure chamber and the suction port of the fan.

[0029] Further, the air-conditioning main unit includes a housing, a negative pressure chamber, an exhaust chamber, a compressor chamber, and a fan; the compressor chamber and the exhaust chamber are arranged side by side outside the same side plate of the negative pressure chamber; the suction port direction of the fan is orthogonal or nearly orthogonal to the main air outlet direction of the finned tube heat exchanger assembly, constructing an air flow vortex chamber between the air outlet of the finned tube heat exchanger assembly in the negative pressure chamber and the suction port of the fan.

[0030] Further, the air-conditioning main unit is composed of modular assemblies. The modules include a compressor cavity provided with a compressor, an external heat exchanger assembly cavity provided with a finned tube heat exchanger assembly and a vertical exhaust chamber, and a longitudinal exhaust chamber communicated with the vertical exhaust chamber; the longitudinal exhaust chamber is arranged below or above the external heat exchanger assembly cavity and is fixedly connected to the bottom plate or the top plate of the vertical exhaust chamber; the compressor cavity is arranged on the side of the longitudinal exhaust chamber of the external heat exchanger assembly cavity and is communicated with the external heat exchanger assembly cavity for the fluorine circuit and the electric circuit; the exhaust port of the longitudinal exhaust chamber has the same orientation as the air inlet of the finned tube heat exchanger assembly.

[0031] Furthermore, the horizontal cross-sectional dimension of the longitudinal exhaust chamber is greater than or equal to the horizontal cross-sectional dimension of the external heat exchanger assembly cavity; the back plate of the external heat exchanger assembly cavity is flush with the back plate of the longitudinal exhaust chamber; the compressor cavity is arranged on the back plate of the longitudinal exhaust chamber of the external heat exchanger assembly cavity.

[0032] An equipment platform is provided with the air-conditioning main unit.

[0033] Compared with the prior art, the present invention has the following beneficial effects:

[0034] 1. Saving the structural materials for refrigerant distribution and collection

[0035] The present invention provides a finned tube heat exchanger assembly that uses a set of liquid collection and distribution lotus heads and gas collection and distribution pipes to implement the "one - to - two" connection of two flat - type finned tube heat exchangers of a copper tube V - shaped finned tube heat exchanger assembly, solving the problems of transporting refrigerant liquid and collecting low - pressure refrigerant vapor in each refrigerant branch of the two flat - type finned tube heat exchangers of the copper tube V - shaped finned tube heat exchanger assembly acting as an evaporator, as well as the problems of distributing high - temperature and high - pressure refrigerant gas and collecting condensate in each refrigerant branch of the two flat - type finned tube heat exchangers of the copper tube V - shaped finned tube heat exchanger assembly acting as a condenser, and saving the materials of the refrigerant distribution and collection structure, namely the lotus head gas collection and distribution pipes.

[0036] 2. Improve the energy efficiency ratio of the refrigeration and air - conditioning system

[0037] The present invention increases the heat release temperature difference and heat release amount in the superheat section of the condenser, increases the sub - cooling degree of the condensate in the sub - cooling section and the heat absorption amount of the evaporator, and can also increase the superheat degree at the outlet of the evaporator of the refrigeration system, improving the operation safety and energy efficiency ratio.

[0038] Through the above - mentioned subversive innovations on the air - side and refrigerant - side, the present invention simplifies the structure of the outdoor heat exchanger of the air - conditioner host, improves the uniformity of the operations of distributing refrigerant liquid (acting as an evaporator) and distributing refrigerant gas (acting as a condenser), and increases the sub - cooling degree of the condensate when acting as a condenser and the superheat degree of the steam when acting as an evaporator, thereby improving the energy efficiency ratio of the refrigeration and air - conditioning system and achieving the intensive design of the air - conditioner host structure and high - load efficient operation.

[0039] The present invention only reverses the inlet and outlet of about half of the refrigerant branches on the finned tube heat exchanger, and realizes the expansion of the fin length between the high - temperature inlet pipe (i.e., the refrigerant gas pipe) and the lowest - temperature liquid outlet pipe (i.e., the refrigerant liquid pipe) on each refrigerant branch, the reduction of the temperature gradient on the fin group, the decrease of the heat conduction intensity along the fin direction, and the further deepening of the "sub - cooling depth" of the condensate at the outlet of the condenser, thereby further enhancing the refrigeration capacity of the evaporator.

[0040] In each refrigerant pipeline module unit of the present invention, the high - temperature inlet pipes and low - temperature liquid outlet pipes on two refrigerant branches are arranged "back - to - back" on different single - row finned tube heat exchangers, weakening the heat conduction of the refrigerant heat across the copper tube along the fin, and strengthening the heat exchange between the refrigerant and the ventilation air flow; the fin heat bridge between the high - temperature inlet pipe and the lowest - temperature liquid outlet pipe on two refrigerant branches in each refrigerant pipeline module unit is disconnected, and the "sub - cooling depth" of the condensate at the outlet of the refrigerant branch is further deepened, thereby further enhancing the refrigeration capacity of the evaporator of the system. Description of the Drawings

[0041] Figure 1The finned tube heat exchanger assembly in an air conditioner main unit with a vertical fan layout and its equipment platform (202310972409.9) in the prior art;

[0042] Figure 2 Schematic diagram of the developed copper tube V-shaped finned tube heat exchanger assembly in Example 1, with a refrigerant crossover pipe connecting the flat finned tube heat exchanger on the other side;

[0043] Figure 3 3D view of the copper tube V-shaped finned tube heat exchanger assembly in Example 1, with a refrigerant crossover pipe connecting the flat finned tube heat exchanger on the other side;

[0044] Figure 4 Schematic diagram of the developed copper tube V-shaped finned tube heat exchanger assembly in Example 2, with a refrigerant crossover pipe connecting the flat finned tube heat exchanger on the other side and the liquid distribution and collection lotus head gas collector set far apart;

[0045] Figure 5 Front view of the single-row finned tube heat exchanger in Example 3;

[0046] Figure 6 Front view of a refrigerant branch pipeline of the single-row finned tube heat exchanger in Example 3;

[0047] Figure 7 Pressure-enthalpy diagram refrigerant cycle analysis for improving the subcooling degree at the end of the condenser, reducing the vaporization ratio of the refrigerant in the throttle valve, and thus increasing the refrigeration capacity of the refrigerant in the evaporator;

[0048] Figure 8 For Figure 6 Schematic diagram of the temperature field during the ventilation and heat transfer operation of a linear finned tube heat exchanger after the fins between the pipelines of a refrigerant branch of the shown single-row finned tube heat exchanger are disconnected and then expanded;

[0049] Figure 9 Comparison of the ventilation and heat transfer temperature fields of two different finned tube heat exchanger structures after the fins between a refrigerant branch of an existing single-row finned tube heat exchanger and an adjacent refrigerant branch pipeline are disconnected and then expanded into a linear finned tube heat exchanger;

[0050] Figure 10 3D view of the copper tube V-shaped finned tube heat exchanger assembly with ultra-high heat transfer efficiency in Example 3, with a refrigerant crossover pipe set and the liquid distribution and collection lotus head and the gas collector for distribution and collection set far apart;

[0051] Figure 11 3D view of the refrigerant crossover pipe of a refrigerant branch of the copper tube V-shaped finned tube heat exchanger assembly with ultra-high heat transfer efficiency in Example 3, with a refrigerant crossover pipe set and the liquid distribution and collection lotus head and the gas collector for distribution and collection set far apart;

[0052] Figure 12 2D developed view of the copper tube N-shaped finned tube heat exchanger assembly with a refrigerant crossover pipe installed for Example 3, and the liquid distribution lotus head and the header pipes are set far apart, having ultra-high heat transfer efficiency;

[0053] Figure 13 Top view of the operating air flow of the copper tube V-shaped finned tube heat exchanger assembly with a refrigerant crossover pipe installed for Example 3, and the liquid distribution lotus head and the header pipes are set far apart, having ultra-high heat transfer efficiency;

[0054] Figure 14 Top view of the air conditioner main unit with the V-shaped finned tube heat exchanger assembly that uses a refrigerant crossover pipe and has the liquid distribution lotus head and the header pipes set far apart for Example 4;

[0055] Figure 15 2D developed view of the copper tube N-shaped finned tube heat exchanger assembly with a refrigerant crossover pipe installed for Example 4, and the liquid distribution lotus head and the header pipes are set far apart, having ultra-high heat transfer efficiency;

[0056] Figure 16 Top view of the operating air flow of the air conditioner main unit with the V-shaped finned tube heat exchanger assembly that uses a refrigerant crossover pipe and has the liquid distribution lotus head and the header pipes set far apart for Example 4

[0057] Figure 17 Schematic structural view of the finned tube heat exchanger with the gaseous interfaces of the refrigerant branch pipes connected in a "back-to-back" manner for Example 5;

[0058] Figure 18 3D perspective view of the compact air conditioner main unit with the finned tube heat exchanger that uses the gaseous interfaces of the refrigerant branch pipes connected to the refrigerant pipes in a "back-to-back" manner for Example 5;

[0059] Figure 19 Top view of the air path structure of the compact air conditioner main unit with the finned tube heat exchanger that uses the gaseous interfaces of the refrigerant branch pipes connected to the refrigerant pipes in a "back-to-back" manner for Example 5;

[0060] Figure 20 Schematic diagram of the refrigerant flow in the operation of the finned tube heat exchanger with the gaseous interfaces of the refrigerant branch pipes connected in a "back-to-back" manner for Example 5;

[0061] Figure 21 Top view of the operating air flow of the compact air conditioner main unit with the finned tube heat exchanger that uses the gaseous interfaces of the refrigerant branch pipes connected to the refrigerant pipes in a "back-to-back" manner for Example 5;

[0062] Figure 22 2D developed view of the copper tube M-shaped finned tube heat exchanger assembly with a refrigerant crossover pipe installed for Example 6, and the liquid distribution lotus head and the header pipes are set far apart, having ultra-high heat transfer efficiency;

[0063] Figure 23 Schematic diagram of a finned tube heat exchanger with the gaseous interfaces and liquid interfaces of two refrigerant branches in the double-row tube heat exchanger of Embodiment 7 arranged "back-to-back".

[0064] Figure 24 Schematic diagram of the air-conditioning main unit of Embodiment 7

[0065] Figure 25 Two-dimensional developed view of the M-shaped finned tube heat exchanger assembly with a refrigerant cross-over pipe arranged in Embodiment 8 and the distributed liquid lotus head and the distributed gas pipe arranged far apart, which has ultra-high heat exchange efficiency

[0066] Figure 26 Schematic diagram of the equipment platform of the three-chamber household-coupled central air-conditioning main unit adopted in Embodiment 9

[0067] Figure 27 Top view of the operating air flow of the equipment platform of the three-chamber household-coupled central air-conditioning main unit adopted in Embodiment 9

[0068] Figure 28 Schematic diagram of the combined commercial air-conditioning main unit system of Embodiment 10

[0069] Figure 29 Top view of the structure of the external heat exchanger assembly of the combined commercial air-conditioning main unit and the structure of the whole-machine refrigeration system of Embodiment 10

[0070] Figure 30 Three-dimensional sectional view of the combined commercial air-conditioning main unit of Embodiment 10

[0071] Figure 31 Vertical sectional view of the operating air flow of the combined commercial air-conditioning main unit of Embodiment 10

[0072] Figure 32 Top view of the air flow operation of the combined commercial coupled air-conditioning main unit on the equipment platform of Embodiment 10 Detailed implementation manners

[0073] To make the objectives, technical solutions and advantages of the present application clearer, the technical solutions of the present application will be clearly and completely described below in conjunction with the drawings of the embodiments of the present application. Obviously, the described embodiments are part of the embodiments of the present application, rather than all of the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the described embodiments without creative efforts shall fall within the scope of protection of the present application.

[0074] Unless otherwise defined, the technical terms or scientific terms used in this application should be understood by people with ordinary skills in the field to which this application belongs. "First", "second" and similar words used in this application do not indicate any order, quantity or importance, but are only used to distinguish different components. "Include" or "comprise" and other similar words mean that the elements or objects appearing before the word include the elements or objects listed after the word and their equivalents, without excluding other elements or objects. "Connect" or "connected" and other similar words are not limited to physical or mechanical connections, but may include electrical connections, whether direct or indirect.

[0075] In the description of the present invention, it is necessary to understand that the terms "horizontal", "longitudinal", "length", "up", "down", "left", "right", etc. indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction. Therefore, they should not be understood as limitations on the present invention.

[0076] Definition: The direction perpendicular to the outer facade of the external corridor type equipment platform is set as the longitudinal direction, and the direction parallel to the outer facade of the external corridor type equipment platform is set as the transverse direction.

[0077] The liquid distributor lotus head and gas distributor pipe of the fin-tube heat exchanger are connected with each branch of the fin-tube heat exchanger, which is the refrigerant distribution and collection mechanism and the main hub for the refrigerant to enter and exit the fin-tube heat exchanger.

[0078] The liquid collecting lotus head is arranged at one end of the fin-tube heat exchanger. When the fin-tube heat exchanger is used as an evaporator, the liquid collecting lotus head is responsible for distributing and delivering the refrigerant liquid to each refrigerant branch of the fin-tube heat exchanger. When the fin-tube heat exchanger is used as a condenser, the liquid collecting lotus head is responsible for reversely collecting the condensate from each refrigerant branch of the condenser.

[0079] The collecting and distributing gas pipe is arranged at one end of the fin-tube heat exchanger. When the fin-tube heat exchanger is used as an evaporator, the collecting and distributing gas pipe is responsible for collecting the low-pressure refrigerant vapor from each refrigerant branch of the evaporator. When the fin-tube heat exchanger is used as a condenser, the collecting and distributing gas pipe is responsible for reversely distributing the high-temperature and high-pressure refrigerant gas from the compressor to each refrigerant branch of the condenser.

[0080] The liquid distribution lotus head and the gas distribution pipe are a pair of coupling devices on the refrigeration pipeline. They are always used together and act together. When one outputs refrigerant, the other is responsible for recovery. When one distributes refrigerant, the other is responsible for collection. The evaporation heat absorption and condensation heat release of the refrigerant occur in each refrigerant branch of the fin-tube heat exchanger between the liquid distribution lotus head and the gas distribution pipe.

[0081] In most scenarios, an even number of refrigerant tubes are used in each refrigerant branch of the finned tube heat exchanger (1 U-shaped tube is equivalent to 2 refrigerant tubes). The liquid distribution and collection lotus head and the gas collector and distributor are arranged adjacent to each other and on the same end face of the finned tube heat exchanger, so as to achieve simple assembly manufacturing process, short connecting pipelines between the four-way valve and the heat exchanger, and reduction of the ineffective pipeline resistance generated by the pipelines that do not participate in heat exchange.

[0082] The flat finned tube heat exchanger includes, but is not limited to, single-row tube, double-row tube, triple-row tube, quadruple-row tube, and quintuple-row tube finned tube heat exchangers.

[0083] As used in this application, the term "copper tube" generally refers to the metal pipeline for transporting refrigerant, which can be one of copper tubes, aluminum tubes, iron tubes, titanium tubes, stainless steel tubes, etc.

[0084] As used in this application, the term "refrigerant gas pipeline" refers to the refrigerant pipeline that is connected to the suction and discharge ports of the compressor through a four-way valve in the finned tube heat exchanger (whether it is a condenser or an evaporator), and is a high-pressure (or low-pressure) refrigerant gas pipeline, that is, a refrigerant gas pipeline.

[0085] As used in this application, the term "refrigerant liquid pipeline" refers to the refrigerant pipeline that is connected (close to) the throttle valve in the finned tube heat exchanger (whether it is a condenser or an evaporator), and is all liquid or mainly liquid, that is, a refrigerant liquid pipeline.

[0086] As used in this application, the term "refrigerant cross-over pipeline" refers to the "copper tube" that connects the refrigerant pipelines of different finned tube heat exchangers.

[0087] Embodiment 1

[0088] This embodiment focuses on the distribution and collection of refrigerant in the copper tube V-shaped finned tube heat exchanger assembly, and solves the problem of how to use only 1 liquid distribution and collection lotus head and 1 gas collector and distributor (hereinafter collectively referred to as "lotus head" and gas collector and distributor), and at the same time solves the problem of refrigerant distribution and recovery of 2 flat finned tube heat exchangers in the V-shaped finned tube heat exchanger assembly.

[0089] As shown in Figures 2 - 3 a finned tube heat exchanger assembly includes 2 flat finned tube heat exchangers 1, 1 liquid distribution and collection lotus head 2, and 1 gas collector and distributor 3;

[0090] The finned tube heat exchanger 1 can be a single-row tube, double-row tube or triple-row tube finned tube heat exchanger 1;

[0091] The flat finned tube heat exchanger 1 includes a number of refrigerant branches 11; the refrigerant branches 11 between different flat finned tube heat exchangers are connected in series through a refrigerant cross-over pipeline 12;

[0092] A number of refrigerant branches 11 are connected to the liquid distribution and collection lotus head 2 and the gas collector and distributor 3 to form a finned tube heat exchanger assembly.

[0093] The liquid distribution lotus head 2 and the liquid-gas collecting pipe 3 are respectively arranged at the same side end plate 13 of the same flat finned tube heat exchanger 1.

[0094] In this embodiment, a set of liquid distribution lotus head 2 and liquid-gas collecting pipe 3 are arranged adjacent to each other at the same side end plate 13 of the flat finned tube heat exchanger 1, directly performing liquid (gas) distribution and gas (liquid) collection for several refrigerant branches 11 in the flat finned tube heat exchanger 1 on the adjacent side, and passing through several refrigerant cross-over pipelines 12 in the flat finned tube heat exchanger on the adjacent side to connect several refrigerant branches 11 in another flat finned tube heat exchanger 1 to perform liquid (gas) distribution and gas (liquid) collection for the operation of these several refrigerant branches 11, simplifying the refrigerant feeding and discharging structure of the finned tube heat exchanger and improving the balance of liquid and gas distribution operations;

[0095] The refrigerant cross-over pipeline 12 in this embodiment can be a copper tube with both ends open pre-implanted before finned tube expansion, or the straight tube part after the elbow of the U-shaped tube is cut after finned tube expansion;

[0096] For each copper tube of several refrigerant branches 11 in the flat finned tube heat exchanger 1 on the adjacent side of the liquid distribution lotus head 2 and the liquid-gas collecting pipe 3 in this embodiment, and each copper tube of several refrigerant branches 11 in another flat finned tube heat exchanger 1 (including the refrigerant cross-over pipeline 12 in the flat finned tube heat exchanger on the adjacent side), the number of copper tubes requisitioned can be different, but the total length of the pipelines on each refrigerant branch 11 is equal or basically equal.

[0097] When the copper tube V-shaped finned tube heat exchanger assembly operates as an evaporator in this embodiment, the liquid distribution lotus head 2 connected to the throttle valve directly distributes and transports the refrigerant liquid for several refrigerant branches 11 in the flat finned tube heat exchanger 1 on the adjacent side, and passes through several refrigerant pipelines 11 in the flat finned tube heat exchanger 1 on the adjacent side to connect several refrigerant branches 11 in another flat finned tube heat exchanger 1 of the copper tube V-shaped finned tube heat exchanger assembly to perform distribution and transportation of the refrigerant liquid for the operation of these several refrigerant branches 11, so as to meet the refrigerant liquid demand for the evaporation heat absorption operation of each refrigerant branch 11 of the copper tube V-shaped finned tube heat exchanger assembly (evaporator). The liquid-gas collecting pipe 3 connected to the suction port of the compressor 4 directly collects the low-pressure refrigerant steam for several refrigerant branches 11 in the flat finned tube heat exchanger 1 on the adjacent side, and passes through several refrigerant pipelines 11 in the flat finned tube heat exchanger 1 on the adjacent side to connect several refrigerant branches 11 in another flat finned tube heat exchanger 1 of the copper tube V-shaped finned tube heat exchanger assembly to collect the low-pressure refrigerant steam for the operation of these several refrigerant branches 11.

[0098] When the copper tube V-shaped finned tube heat exchanger assembly of this embodiment operates as a condenser, the header pipe 3 connected to the exhaust pipe of the compressor 4 directly distributes high-temperature and high-pressure refrigerant gas to several refrigerant branches 11 in the adjacent flat finned tube heat exchanger 1, and through several refrigerant pipelines 11 in the adjacent flat finned tube heat exchanger 1, it is connected to several refrigerant branches 11 in the other flat finned tube heat exchanger 1 of the copper tube V-shaped finned tube heat exchanger assembly to distribute high-temperature and high-pressure refrigerant gas for the operation of these several refrigerant branches 11, so as to meet the refrigerant gas demand for condensation heat release of each refrigerant branch of the copper tube V-shaped finned tube heat exchanger assembly (condenser); the liquid-gas separator lotus head 2 connected to the throttle valve directly collects the condensate of several refrigerant branches 11 in the adjacent flat finned tube heat exchanger 1, and through several refrigerant pipelines in the adjacent flat finned tube heat exchanger 1, it is connected to several refrigerant branches 11 in the other flat finned tube heat exchanger 1 of the copper tube V-shaped finned tube heat exchanger assembly to collect the condensate of these several refrigerant branches 11.

[0099] Due to the innovative setting of the "refrigerant bypass pipeline 12" in this embodiment, it has significant technical significance and commercial value:

[0100] (1) Simplify the complex

[0101] This embodiment simplifies the complex. By only using a set of liquid-gas separator lotus head 2 and header pipe 3 to implement "one-driving-two" connection to the 2 flat finned tube heat exchangers of the copper tube V-shaped finned tube heat exchanger assembly, it simultaneously solves the problems of transporting refrigerant liquid and collecting low-pressure refrigerant steam in each refrigerant branch 11 of the 2 flat finned tube heat exchangers 1 of the copper tube V-shaped finned tube heat exchanger assembly as an evaporator, as well as the problems of distributing high-temperature and high-pressure refrigerant gas and collecting condensate in each refrigerant branch 11 of the 2 flat finned tube heat exchangers 1 of the copper tube V-shaped finned tube heat exchanger assembly as a condenser.

[0102] (2) Reduce risks

[0103] When the finned tube heat exchanger 1 is used as an evaporator, the refrigerant transported from the throttle valve outlet to the evaporator is not a single-phase condensate but a gas-liquid two-phase flow, and the gas-liquid ratio also varies with the working conditions. Implementing the precise distribution of the liquid-phase refrigerant in the gas-liquid two-phase flow faces great risks and difficulties.

[0104] In this embodiment, only one set of liquid - distributing lotus - head 2 and gas - collecting and distributing pipe 3 are used to serve two flat - type finned - tube heat exchangers of the copper - tube V - type finned - tube heat exchanger assembly, reducing the material consumption and welding workload of the liquid - distributing lotus - head 2 and gas - collecting and distributing pipe 3, reducing the pipeline welding points and possible refrigerant leakage points; in particular, this embodiment overcomes the risk of uneven two - stage liquid refrigerant distribution brought by the two - stage refrigerant distribution technical solution composed of two liquid - distributing lotus - heads and two gas - collecting and distributing pipes.

[0105] Embodiment 2

[0106] As Figure 4 shown, a finned - tube heat exchanger assembly includes two flat - type finned - tube heat exchangers 1, one liquid - distributing lotus - head 2 and one gas - collecting and distributing pipe 3;

[0107] The finned - tube heat exchanger 1 can be a single - row tube, double - row tube or triple - row tube finned - tube heat exchanger 1;

[0108] The flat - type finned - tube heat exchanger 1 includes a number of refrigerant branches 11; the refrigerant branches 11 between different flat - type finned - tube heat exchangers 1 are connected in series through refrigerant cross - over pipelines 12;

[0109] The refrigerant branches 11 are connected to the liquid - distributing lotus - head 2 and the gas - collecting and distributing pipe 3 to form a finned - tube heat exchanger assembly.

[0110] The liquid - distributing lotus - head 2 and the gas - collecting and distributing pipe 3 are respectively arranged at the end plates 13 of different flat - type finned - tube heat exchangers 1.

[0111] This embodiment is similar to Embodiment 1 in that both use one set of liquid - distributing lotus - head 2 and gas - collecting and distributing pipe 3 to serve two flat - type finned - tube heat exchangers 1 of the copper - tube V - type finned - tube heat exchanger assembly.

[0112] The difference of this embodiment is that one set of liquid - distributing lotus - head 2 and gas - collecting and distributing pipe 3 are arranged far apart at both ends of the copper - tube V - type finned - tube heat exchanger assembly to perform liquid (gas) - distributing and gas (liquid) - collecting for a number of refrigerant branches 11 in multiple flat - type finned - tube heat exchangers 1, and through a number of refrigerant cross - over pipelines 12 between the flat - type finned - tube heat exchangers 1, the number of refrigerant branches 11 distributed in multiple flat - type finned - tube heat exchangers 1 are connected together to perform liquid (gas) - distributing and gas (liquid) - collecting for the operation of this number of refrigerant branches 11, simplifying the refrigerant feeding and discharging structure of the finned - tube heat exchanger 1 and improving the balance of the liquid - distributing and gas - distributing operations.

[0113] For the number of refrigerant branches 11 in multiple flat - type finned - tube heat exchangers 1 where the liquid - distributing lotus - head 2 and the gas - collecting and distributing pipe 3 are arranged far apart in this embodiment, the total length of the copper - tube pipelines on each refrigerant branch 11 is kept equal or approximately equal.

[0114] This embodiment has all the advantages of Embodiment 1. Moreover, since a set of liquid-distributing lotus heads 2 and liquid-gas collecting pipes 3 are distantly arranged at both ends of the copper tube V-shaped (or N-shaped, or M-shaped) finned tube heat exchanger assembly, an optimized arrangement scheme of the finned tube heat exchanger pipeline is achieved, where the liquid pipe interfaces on the liquid-distributing lotus heads 2 of each refrigerant branch 11 are distantly arranged from the gas pipe interfaces on the liquid-gas collecting pipes 3, the gaseous high-temperature refrigerant copper tubes of each refrigerant branch 11 are adjacently arranged, and the liquid low-temperature refrigerant pipelines of each refrigerant branch 11 are adjacently arranged. While fully leveraging the advantage of the finned tube heat exchanger 1 in increasing the heat exchange area of the refrigerant pipeline, it solves the problem that the condenser in Embodiment 1 usually has, where the high-temperature and high-pressure refrigerant gas conducts heat through the fin thermal bridge to the condensate in the copper tube in the subcooling heat release stage, hindering the deep subcooling of the condensate and reducing the refrigeration capacity of the evaporator.

[0115] Embodiment 3

[0116] As Figures 5 - 13 , this embodiment makes a subversive innovation to the structure of the finned tube heat exchanger assembly, constructing a V (N, M)-shaped finned tube heat exchanger assembly with a refrigerant cross-over pipeline 12 and the liquid-distributing lotus heads 2 and liquid-gas collecting pipes 3 distantly arranged, which has extremely high heat exchange efficiency.

[0117] This embodiment first analyzes the heat transfer process and characteristics of the finned tube heat exchanger 1, as well as the relationship between the deep subcooling of the condensate and the refrigeration capacity of the evaporator:

[0118] The structure of the finned tube heat exchanger 1, as Figures 5 - 6 shown, selects the middle branch for in-depth dissection and analysis; the finned tube heat exchanger 1 made of copper tubes expanded and connected to aluminum fins is essentially a good heat conductor structure and a metal framework with the characteristic of temperature equilibrium;

[0119] As a heat exchanger between the refrigerant and air, the finned tube structure of copper tubes expanded and connected to aluminum fins has two functions:

[0120] ① Heat transfer enhancement function

[0121] Since the air has low density and small specific heat capacity, in the three-stage heat transfer path perpendicular to the copper tube of the refrigerant (mainly in two-phase flow pattern) - copper tube wall - aluminum fin - air flow inside the copper tube, the thermal resistance mainly occurs on the air flow side; expanding aluminum fins on the outside of the copper tube to form a finned tube is to effectively increase the convective heat transfer area and heat transfer coefficient of the copper tube to the air flow and enhance the heat transfer function of the copper tube;

[0122] ② Thermal bridge function

[0123] The fin group on the fin-tube heat exchanger 1 also has a heat bridge function for conducting heat, and conducts the heat of the copper tube where the high-temperature refrigerant is located to the refrigerant in the copper tube with a relatively low temperature through the fin group heat bridge; for example, for the heat transfer temperature difference between the refrigerant flow and the air flow in the condenser, the aluminum fin group reduces the temperature difference between the high-temperature refrigerant pipeline and the air flow in the superheated heat release section of each branch (flow path), and increases the temperature difference between the low-temperature refrigerant pipeline and the air flow in the subcooled heat release section, and plays a role in "peak shaving and valley filling" for different heat transfer temperature difference areas of the fin tube; this "thermal bridge function" of the fin tube is a "by-product" function of the fin tube structure, which is not conducive to enhanced heat exchange;

[0124] Generally, the design and use of the fin-tube heat exchanger 1 in air-conditioning engineering needs to ensure and enhance the heat exchange function and suppress or even eliminate the thermal bridge function.

[0125] Comparative Example:

[0126] When the existing fin-tube heat exchanger 1 is operated as a condenser, the heat of the high-temperature and high-pressure refrigerant gas in the tube at the head of each refrigerant branch 11 is released to the air (ventilation airflow) through the copper tube and the fins outside the tube, and is also transferred to the condensate in the terminal pipeline adjacent to the refrigerant branch 11 through the fin heat bridge; in particular, the pipeline at the end (subcooling section) of each refrigerant branch 11 is adjacently connected to the inlet pipeline of the high-temperature refrigerant gas of the next branch through the fins, and while the fin group connected to the copper tube of the subcooling section strengthens the "subcooling heat release" of the ventilation airflow, it is also passively The heat is transferred from the high-temperature and high-pressure refrigerant gas in the inlet pipe of the next refrigerant branch 11 adjacent to the condenser through the fin heat bridge. The fin heat bridge is very short and the conduction temperature difference is extremely large (up to 50°C or more). As a result, the condensate in the subcooling section releases heat to the ventilation airflow through the fin group and absorbs heat from the high-temperature and high-pressure refrigerant gas through the fin heat bridge. This makes it difficult to implement the "subcooling operation" deeply. The condensate at the condenser outlet is insufficiently "subcooled", which increases the "dryness" of the refrigerant at the throttle valve outlet and reduces the heat absorption of the condensate entering the evaporator and the heat release of the condenser.

[0127] Similarly, when the fin-tube heat exchanger 1 operates as an evaporator, the refrigerant two-phase flow in the evaporation section also absorbs heat from the superheated section at the end of the evaporator through the fin heat bridge, thereby reducing the "superheat" of the refrigerant vapor at the evaporator outlet, reducing the heat absorption of the evaporator and the heat release of the condenser.

[0128] The data on standard test conditions for air-conditioning compressors also proves the above situation.

[0129] The internationally recognized standard test conditions for air conditioner compressors refer to the air conditioner standard test conditions of "under the condition of an ambient temperature of 35°C, the condensation temperature of the condenser in the air conditioning system is 54.4°C, the subcooling degree of the condensate is 8.3°C, the evaporation temperature of the evaporator is 7.2°C, and the superheat degree of the low-pressure steam in the evaporator is 11.1°C"; under this standard test condition, the condensate at the end of the condenser cooled by the 35°C ambient air can only be subcooled to 46.1°C, and the subcooling degree is only 8.3°C; under the cross-flow heat exchange operation, in the face of the 35°C heat-absorbing air, the condensate at the outlet of the condenser can only be reduced to 46.1°C, which is more than 11°C higher than the temperature of the cooling medium (ambient air) of 35°C. This fully proves that the overall isothermal characteristic of the current copper-aluminum metal structure of the finned tube condenser has a very strong resistance to "subcooled heat release of condensate".

[0130] Further analysis of this embodiment is as follows Figure 8 As shown, the following problems are found in the three-stage heat release along the pipeline direction of a refrigerant branch 11 (sub-heat exchanger) of the existing single-piece finned tube heat exchanger (condenser):

[0131] The three-stage heat exchange temperature field of a branch (sub-heat exchanger, with continuous fins and complete fin heat bridges) among multiple refrigerant branches 11 of the existing single-row finned tube heat exchanger (condenser), unfolded along the pipeline length direction:

[0132] a→b is the superheat heat release section, corresponding to the head of the condenser, releasing the sensible heat of the high temperature of the high-temperature and high-pressure refrigerant gas discharged by the compressor. The main body of the heat comes from the compression work of the compressor; since the fin group in this section transfers heat to the finned tubes in the nearby low-temperature area through the fin heat bridge while releasing heat to the ventilation air flow, the wall temperature of the finned tubes in this section is pulled down, and the heat transfer temperature difference to the ventilation air flow is reduced, resulting in a reduction in the direct heat release of the finned tubes in this section to the ventilation air flow and transferring part of the load to the relatively low-temperature finned tubes in the adjacent area through the fin heat bridge;

[0133] b→c is the condensation heat release section, corresponding to the middle part of the condenser, releasing the condensation phase change heat of the high-pressure refrigerant gas. The main body of the heat comes from the heat absorption of the evaporator in the low-temperature area;

[0134] The section from c to d is the subcooling heat release section, corresponding to the end of the condenser, which releases the sensible heat of the high-pressure condensate. The main source of heat is the heat absorption of the evaporator in the low-temperature area. The pipeline at the end (subcooling section) of each refrigerant branch 11 is connected to the inlet pipeline of the high-temperature refrigerant gas of the next refrigerant branch 11 through fins, and passively receives the heat conducted by the high-temperature and high-pressure refrigerant gas in the inlet pipeline of the adjacent next refrigerant branch 11 through the fin heat bridge. Moreover, the length of the fin heat bridge is very short and the conduction temperature difference is extremely large (up to more than 50 °C), resulting in that the condensate in the subcooling section is both subcooling and releasing heat to the ventilation air flow through the fin group and being heated by the high-temperature and high-pressure refrigerant gas in the adjacent branch through the fin heat bridge, making it difficult to deeply implement the "subcooling operation".

[0135] Such as Figures 5 - 13 , this embodiment innovatively proposes:

[0136] A finned tube heat exchanger assembly, comprising 3 flat finned tube heat exchangers 1, 1 liquid distribution lotus head 2 and 1 gas collector and distributor 3;

[0137] The finned tube heat exchanger 1 can be a single-row tube, double-row tube or triple-row tube finned tube heat exchanger 1;

[0138] The flat finned tube heat exchanger 1 includes several refrigerant branches 11; the refrigerant branches 11 between different flat finned tube heat exchangers 1 are connected in series through refrigerant bypass pipelines 12;

[0139] The refrigerant branch 11 connects the liquid distribution lotus head 2 and the gas collector and distributor 3 to form a finned tube heat exchanger assembly.

[0140] The liquid distribution lotus head 2 and the gas collector and distributor 3 are respectively arranged at the end plates 13 of different flat finned tube heat exchangers 1.

[0141] Any refrigerant branch 11 between the liquid distribution lotus head 2 and the gas collector and distributor 3 is segmented and arranged in each flat finned tube heat exchanger 1.

[0142] The total length of the refrigerant pipelines of any refrigerant branch 11 between the liquid distribution lotus head 2 and the gas collector and distributor 3 is equal or basically equal.

[0143] The adjacent flat finned tube heat exchangers 1 are connected to the refrigerant branches 11 through the refrigerant bypass pipelines 12, and the superheat heat exchange section, phase change heat exchange section and subcooling heat exchange section of any refrigerant branch 11 between the gas collector and distributor 3 and the liquid distribution lotus head 2 are distributed in each flat finned tube heat exchanger 1.

[0144] Structurally, in this embodiment, starting from the liquid - collecting lotus head 2, through a number of fine - diameter liquid - distributing pipes, it is connected to the pipe orifices and pipelines corresponding to several refrigerant branches on the end plate of the first flat - finned tube heat exchanger 1 adjacent to the side of the liquid - collecting lotus head 2. Then, through a number of refrigerant cross - over pipelines 12, it is sequentially cross - connected to the corresponding pipe orifices and pipelines of several refrigerant branches on the second / third flat - finned tube heat exchanger 1 until it is sequentially cross - connected to the corresponding pipelines and pipe orifices on the flat - finned tube heat exchanger 1 on the other side adjacent to the gas - collecting and distributing pipe 3 through a number of refrigerant cross - over pipelines 12, and finally connected to the gas - collecting and distributing pipe 3.

[0145] This embodiment only uses a set of liquid - collecting lotus head 2 and gas - collecting and distributing pipe 3 to perform liquid (gas) separation and gas (liquid) collection for each refrigerant branch 11 arranged on 2 / 3 / 4 flat - finned tubes of the finned - tube heat exchanger assembly. Moreover, the liquid - collecting lotus head 2 and the gas - collecting and distributing pipe 3 are arranged on different sides, that is, far from each other, and are arranged on two sides of the finned - tube heat exchanger assembly. This embodiment simplifies the structure of the external heat exchanger, improves the uniformity of the operation of distributing the refrigerating liquid (as an evaporator) and distributing the refrigerant gas (as a condenser), and also improves the sub - cooling degree of the condensate when used as a condenser and the superheat degree of the steam when used as an evaporator.

[0146] This embodiment further analyzes the relationship between the deep sub - cooling of the condensate in the refrigeration system and the refrigerating capacity of the evaporator:

[0147] The refrigerating capacity of the evaporator in the refrigeration system is the product of the refrigerant circulation rate and the enthalpy difference of the refrigerant at the inlet and outlet of the evaporator. The enthalpy difference of the refrigerant at the inlet and outlet of the evaporator is negatively correlated with the "dryness" of the refrigerant entering the evaporator inlet from the throttle valve outlet.

[0148] The dryness of the refrigerant at the evaporator inlet is the proportion of the gaseous refrigerant at the throttle valve outlet in the refrigerant gas - liquid two - phase flow. The lower the dryness, that is, the closer the dryness is to 0, the lower the gaseous proportion (close to 0) and the higher the liquid proportion (close to 1.0). The "completeness" of the evaporation of the refrigerating liquid in the evaporator is high, the enthalpy difference of the refrigerant at the inlet and outlet of the evaporator is large, and the refrigerating capacity of the evaporator is large. On the contrary, the higher the dryness of the refrigerant at the evaporator inlet, that is, the closer the dryness is to 1, the higher the gaseous proportion (close to 1) and the lower the liquid proportion (close to 0). The "completeness" of the evaporation of the refrigerating liquid in the evaporator is low, the enthalpy difference of the refrigerant at the inlet and outlet of the evaporator is small, and the refrigerating capacity is small.

[0149] The "dryness" of the refrigerant at the throttle valve outlet, which is also the inlet of the evaporator, is determined by the "subcooling degree" of the refrigerant liquid at the end of the condenser: During the throttling and pressure reduction process of the refrigerant in the throttle valve, in order to reduce the temperature of the high-pressure and high-temperature condensate at the condenser outlet (i.e., the throttle valve inlet) to the saturation temperature corresponding to the low-pressure state at the throttle valve outlet (i.e., the evaporator inlet), a part of the condensate vaporizes successively during the throttling process of the throttle valve. By the endothermic vaporization of a small part of the condensate, the temperature of most of the condensate is reduced. As a result, the refrigerant injected from the throttle valve outlet into the evaporator inlet is not a liquid refrigerant with a dryness of 0, but a gas-liquid two-phase flow with a dryness of x. The dryness x can be 0.2 (liquid proportion 0.8), 0.3 (liquid proportion 0.7), or 0.4 (liquid proportion 0.6) or even 0.5 (liquid proportion 0.5).

[0150] The dryness x of the refrigerant at the throttle valve outlet and the evaporator inlet is determined by the "subcooling degree" of the condensate at the end of the condenser: If the condensate at the end of the condenser releases heat sufficiently and the temperature drops significantly (much lower than the condensation temperature), it means that the "subcooling degree" of the condensate is high. When it enters the evaporator through the throttle valve, the temperature difference between the condensate temperature at the end of the condenser and the evaporation temperature is small, and the heat release is small. As a result, the proportion of the refrigerant that vaporizes by "phase change" and absorbs heat during the throttling process in the throttle valve is relatively low, and the dryness x of the refrigerant at the evaporator inlet is correspondingly relatively low. When x is as low as 0.2 or even below 0.2, the liquid phase proportion in the refrigerant two-phase flow entering the evaporator is relatively large, and the refrigeration capacity of the evaporator is relatively large; conversely, if the condensate at the end of the condenser does not release heat sufficiently and the temperature is relatively high (not dropping significantly relative to the condensation temperature), that is, the "subcooling degree" of the condensate is low, then the temperature difference between the condensate temperature at the end of the condenser and the evaporation temperature when it enters the evaporator through the throttle valve is large, and the heat release is large. As a result, the proportion of the condensate that vaporizes by "phase change" and absorbs heat when passing through the throttle valve is relatively high, and the dryness x of the refrigerant at the evaporator inlet is correspondingly relatively high. When x reaches 0.3 or even above 0.4, the liquid phase proportion in the refrigerant two-phase flow entering the evaporator is relatively low, and the refrigeration capacity of the evaporator is relatively small.

[0151] This embodiment closely adheres to the core concept of "reducing the dryness of the refrigerant two-phase flow at the throttle valve outlet". The technical solution of this embodiment improves the subcooling degree of the condensate at the end of the condenser, reduces the vaporization proportion of the condensate in the throttle valve, reduces the dryness of the refrigerant two-phase flow at the throttle valve outlet, increases the liquid phase proportion of the refrigerant at the evaporator inlet, and significantly improves the refrigeration capacity of the evaporator.

[0152] In this embodiment, a finned tube heat exchanger assembly with a super-high heat transfer efficiency, which is provided with a refrigerant cross-over pipeline 12 and the liquid distribution and collection lotus head 2 and the gas collector and distributor 3 are arranged far apart, not only solves the problem of connecting the refrigerant pipelines of the copper tube N-shaped finned tube heat exchanger assembly, but also greatly increases the subcooling degree of the condensate, thereby increasing the refrigerating capacity of the evaporator and the heat release of the condenser. Now, taking an air-conditioning system using R410A refrigerant under standard test conditions as an example, the increase in refrigerating capacity brought by the technical solution of this embodiment is calculated as follows:

[0153] ① At an evaporation pressure of 10 atm, the evaporation temperature of R410a is 7.28 °C (close to 7.2 °C under standard test conditions). Assuming the dryness of the refrigerant at the inlet of the evaporator is 0.2, the enthalpy difference per unit mass of the refrigerant between the inlet and outlet of the evaporator (evaporation heat absorption) = (422.89 - 211.09) × 0.8 = 211.8 × 0.8 = 169.44 kj / kg;

[0154] ② At a condensation pressure of 34.0 atm, the condensation temperature of R410A is 54.61 °C (close to 54.4 °C under standard test conditions). The enthalpy difference per unit mass of the refrigerant between the inlet and outlet of the condenser (heat release) = 418.47 - 294.67 = 123.8 kj / kg, and the mass heat capacity of the refrigerant liquid is 2.49 kj / kg;

[0155] ③ In this embodiment, at an ambient temperature of 35 °C, the condensate at the end of the condenser can be easily subcooled to 38 °C, increasing the subcooling degree by 8 °C compared with 46.1 °C under standard test conditions, and increasing the enthalpy difference (heat release) of the condenser by 2.49 × 8 = 19.92 kj / kg;

[0156] ④ The "subcooling" heat release of the condensate at the end of this condenser in this embodiment reduces the dryness of the refrigerant at the outlet of the throttle valve and increases the liquid phase ratio of the refrigerant entering the evaporator, thereby increasing the refrigerating capacity of the evaporator by about 11.8%.

[0157] This embodiment analyzes the heat transfer process of the finned tube heat exchanger assembly structure with the fin heat bridge disconnected:

[0158] For a single-row copper tube-aluminum fin heat exchanger composed of multiple refrigerant branches 11, and each refrigerant branch 11 is composed of multiple pipelines, one of the refrigerant branches 11 (sub-heat exchanger) is separated, and the fins between the pipelines forming this refrigerant branch 11 are disconnected for ventilation heat transfer tests; for the convenience of illustration and analysis, in this embodiment, the pipelines on the same refrigerant branch 11 with the fins disconnected are unfolded into a linear finned tube heat exchanger 1 on the drawing, and its temperature field structure during ventilation heat transfer operation is as follows. Compared with the corresponding temperature field of a single branch of the existing finned tube heat exchanger 1 (the fins are not disconnected and the fin heat bridge is complete), there are huge differences.

[0159] The three-stage heat release of a refrigerant branch 11 with fins disconnected between pipelines in this embodiment:

[0160] As Figure 9 shown, isolate a refrigerant branch 11 of the finned tube heat exchanger 1, disconnect the fins between the pipelines that make up this refrigerant branch 11, and conduct a ventilation heat exchange test. Then, the three-stage temperature field structure along the pipe length direction during its ventilation heat exchange operation is different from the "three-stage temperature field structure" of the heat of the enhanced copper tube heat exchange section in Embodiment 3 along "refrigerant in the tube - copper tube aluminum fins - air flow between fins". Compared with the heat exchange temperature field structure of a single refrigerant branch 11 of the existing finned tube heat exchanger 1 with the fins not disconnected and the fin heat bridge intact in the comparative example, a huge change has occurred:

[0161] a ， →b ， is the superheat heat release section of a refrigerant branch 11 of the condenser with the fin heat bridge disconnected, corresponding to the head of the condenser, releasing the sensible heat of the high-temperature and high-pressure refrigerant gas discharged from the compressor. The main source of heat is the compression work of the compressor; because the fin heat bridge is disconnected, the heat of the high-temperature and high-pressure refrigerant gas in this section of the pipeline does not conduct to the low-temperature area through the fin heat bridge, so the heat transfer temperature difference with the ambient air temperature is large and the heat release is large; the increase in the heat release in this section also causes the starting point of the high-pressure refrigerant gas condensation process to move towards the condenser inlet (b→b ， ).

[0162] b ， →c ， is the condensation heat release section of a refrigerant branch 11 of the condenser with the fin heat bridge disconnected, corresponding to the middle of the condenser, releasing the condensation phase change heat of the high-pressure refrigerant gas. The main source of heat is the heat absorption of the evaporator in the low-temperature area; because the starting point of the high-pressure refrigerant gas condensation in the superheat heat release section moves towards the condenser inlet (b→b ， ), it also causes the end point of the high-pressure refrigerant gas condensation phase change to move towards the condenser inlet (c→c ， ).

[0163] c ， →d ， is the subcooling heat release section of a refrigerant branch 11 of the condenser with the fin heat bridge disconnected, corresponding to the end of the condenser, releasing the sensible heat of the high-pressure condensate. The main source of heat is the heat absorption of the evaporator in the low-temperature area; because the end point of the high-pressure refrigerant gas condensation phase change in the condensation heat release section moves towards the condenser inlet (c→c ， ), it expands the pipeline length and fin area of the subcooling heat release section. Coupled with the fact that the fins are disconnected and there is no heat conduction from the adjacent high-temperature area along the fin heat bridge to the finned tubes in this section, the subcooling heat release effect of this section is improved, and "deep subcooling" of the condensate is achieved, and the state corresponding point changes from d→d， , the degree of undercooling also expands from ⊿T to ⊿T ， .

[0164] For the pipelines of several refrigerant branches 11, the number of pipelines arranged on each flat finned tube heat exchanger 1 can be equal or unequal. The number of copper tubes arranged for each refrigerant branch 11 on each flat finned tube heat exchanger 1 can be complementarily set, and the total length of the copper tubes of each refrigerant branch 11 on each flat finned tube heat exchanger 1 is equal or basically equal.

[0165] In this embodiment, an N-shaped finned tube heat exchanger assembly with ultra-high heat exchange efficiency, which is provided with a refrigerant cross-over pipeline 12 and the liquid distribution and collection lotus head 2 and the gas distribution and collection pipe 3 are arranged far apart, has the following innovation points:

[0166] ① Set the refrigerant cross-over pipeline 12 to penetrate the fluorine circuit of the 3 flat finned tube heat exchangers 1 of the N-shaped finned tube heat exchanger assembly, and separate the liquid distribution and collection lotus head 2 and the gas distribution and collection pipe 3 and set them on both sides of the N-shaped finned tube heat exchanger assembly;

[0167] ② Set the superheat heat release section, the condensation heat release section, and the subcooling heat release section of each refrigerant branch 11 on the 1st / 2nd / 3rd flat finned tube heat exchanger 1 respectively. That is, the main body of the superheat heat release section of each refrigerant branch 11 is centrally arranged (or basically arranged) on the 1st flat finned tube heat exchanger 1, the main body of the condensation heat release section of each refrigerant branch 11 is centrally arranged (or basically arranged) on the 2nd flat finned tube heat exchanger 1, and the main body of the subcooling heat release section of each refrigerant branch 11 is centrally arranged (or basically arranged) on the 3rd flat finned tube heat exchanger 1, so that the refrigerant temperatures of the corresponding sections of each refrigerant branch 11 on each flat finned tube heat exchanger 1 are relatively close, and the heat conduction intensity of the refrigerant heat in the fin direction perpendicular to the copper tube is greatly reduced. It not only retains the advantage of the fin group expanding the surface area of the copper tube and strengthening the heat transfer on the air side, but also is equivalent to cutting off the fin heat bridge from the midpoint of the adjacent copper tubes and blocking the transfer of part of the heat load from the high-temperature area finned tubes to the adjacent low-temperature area finned tubes through the fin heat bridge, solving the problem that it is difficult to deeply implement the "subcooling operation".

[0168] This embodiment increases the heat release temperature difference and the heat release amount in the superheat section of the condenser, increases the subcooling degree of the condensate in the subcooling section and the heat absorption amount of the evaporator, and can also increase the superheat degree at the outlet of the evaporator when the refrigeration system is used as a heat pump, improving the operation safety and the energy efficiency ratio.

[0169] Embodiment 4

[0170] As Figures 14 - 16 shown, this embodiment discloses an air-conditioning main unit including a housing 5, a negative pressure chamber 6, an exhaust chamber 7, a compressor chamber 8, the finned tube heat exchanger assembly of Embodiment 2, and a fan 9;

[0171] The compressor chamber 8 and the exhaust air chamber 7 are arranged side by side on the outside of the same first side plate 54 of the negative pressure chamber 6.

[0172] The air outlet 71 of the exhaust air chamber 7 is arranged on the opposite side of the main air inlet 101 of the air inlet chamber 10 of the housing 5. The opposite side arrangement means that the air outlet 71 and the main air inlet 101 face the same direction. For example, both the air outlet 71 and the main air inlet 101 are arranged on the short side of the housing.

[0173] The suction port direction of the fan 9 is orthogonally arranged or nearly orthogonally arranged with the main air outlet direction of the finned tube heat exchanger assembly, creating an air flow vortex chamber between the air outlet of the finned tube heat exchanger assembly in the negative pressure chamber 6 and the suction port of the fan 9;

[0174] In the exhaust air chamber 7, the fan 9 is arranged at one end close to its air outlet 71; the air outlet of the fan 9 faces directly the air outlet 71 of the exhaust air chamber 7; the air outlet 71 of the exhaust air chamber 7 is a vertical strip-shaped air outlet;

[0175] The fan 9 is a centrifugal fan; preferably, a backward centrifugal fan is adopted; the area of the exhaust air surface on the outer periphery of the fan impeller is 2 to 8 times the area of the suction port of the fan 9.

[0176] The air conditioner main unit of this embodiment is provided with 3 vertically arranged fans 9.

[0177] The finned tube heat exchanger assembly is arranged in the air inlet chamber 10 of the housing 5;

[0178] The finned tube heat exchanger assembly includes a copper tube V-shaped finned tube heat exchanger. The copper tube V-shaped finned tube heat exchanger is an asymmetric copper tube V-shaped finned tube heat exchanger with unequal lengths on both sides, and is composed of 2 flat plate finned tube heat exchangers 1 with different lengths;

[0179] Among them, the long flat plate finned tube heat exchanger 1 is close to the outer side plate 53 of the housing 5; the short flat plate finned tube heat exchanger 1 is close to the first side plate 54 of the exhaust air chamber 7.

[0180] The air inlet chamber 10 of the housing 5 is also provided with an air supply slit 51; the air supply slit 51 is arranged on the housing 5 close to the outer side plate 53 of the long flat plate finned tube heat exchanger 1.

[0181] The suction port of the fan 9 and the air guiding panel are wedged into the negative pressure chamber 6, and a part of the space of the compressor chamber 8 is wedged into the negative pressure chamber 6.

[0182] For the air conditioner main unit in this embodiment, the air duct adopts the technology that the air outlet direction of the finned tube heat exchanger is orthogonal to the air suction port direction of the fan 9, and the air inlet and air outlet are set far apart. The refrigerant circuit adopts the technology of the finned tube heat exchanger assembly with an unbalanced V-shaped finned tube heat exchanger assembly, the refrigerant bridging pipeline 12, the liquid distributing and collecting lotus head 2 and the gas collecting and distributing pipe 3 set far apart, creating a brand-new structure of the air duct flow field, refrigerant circuit flow field and temperature field, promoting the simplification and high efficiency of the main unit structure, and realizing the structural coupling, air duct coupling and energy coupling between the air conditioner main unit and the equipment platform.

[0183] On the air duct side, this embodiment adopts the air duct technology in which the air suction port direction of the fan 9 is orthogonal (or nearly orthogonal) to the air outlet direction of the finned tube heat exchanger 1. The space between the heat exchanger air outlet and the air suction port of the backward centrifugal fan 9 becomes a buffer air flow vortex chamber on the external heat exchanger air duct, a structural conversion area and a functional conversion area on the air duct, and a buffer chamber for decelerating, boosting pressure, adjusting and reorganizing the air flow out of the external heat exchanger;

[0184] On the air duct side, this embodiment connects the air inlet chamber and the negative pressure chamber 6 of the external heat exchanger of the air conditioner main unit in series, and then connects them in series with the exhaust chamber 7 through the fan 9. The air inlet chamber, the negative pressure chamber 6 and the exhaust chamber 7 are arranged in sequence; in the exhaust chamber 7, the circumferential surface of the impeller of the backward centrifugal fan 9 faces the air outlet of the exhaust chamber 7; on the outside of the exhaust chamber 7 facing away from the air outlet, a compressor chamber 8 is arranged; and the compressor chamber 8 and the centrifugal fan 9 chamber are arranged at the rear and side by side, greatly reducing or even zeroing the longitudinal exhaust chamber 7 outside the fan 9, thereby greatly reducing the size, structure and volume of the air conditioner main unit.

[0185] On the refrigerant circuit side, it adopts the finned tube heat exchanger assembly technology with ultra-high heat exchange efficiency in Embodiment 2, which sets the refrigerant bridging pipeline 12 and the liquid distributing and collecting lotus head 2 and the gas collecting and distributing pipe 3 far apart. Only one set of liquid distributing and collecting lotus head 2 and gas collecting and distributing pipe 3 is used to implement liquid (gas) distribution and gas (liquid) collection for each refrigerant branch 11 of the copper tube V-shaped finned tube heat exchanger assembly arranged on 2 flat plate finned tube heat exchangers 1; moreover, the liquid distributing and collecting lotus head 2 and the gas collecting and distributing pipe 3 are arranged on different sides, that is, far apart, and are arranged on the two side edges of the two finned tube heat exchangers 1 of the V-shaped finned tube heat exchanger assembly.

[0186] From the perspective of the refrigerant circuit structure, in this embodiment, starting from the liquid distributing and collecting lotus head 2, through several thin-diameter liquid distribution pipes, it is connected to the pipe orifices and pipelines corresponding to several refrigerant branches 11 on the end plate 13 of the first flat plate finned tube heat exchanger adjacent to the liquid distributing and collecting lotus head 2, and then sequentially connected to the corresponding pipe orifices and pipelines of several refrigerant branches 11 on the second flat plate finned tube heat exchanger 1 through several refrigerant bridging pipelines 12, and finally connected to the gas collecting and distributing pipe 3;

[0187] On the fluorine circuit side, in this embodiment, the technology of arranging the refrigerant branch pipelines 11 in the plate fin tube heat exchanger 1 of the adjacent header manifold 3 "back to back" is also adopted. When used as the end of the condenser, since the inlet pipes of the condensate of two adjacent refrigerant branches 11 are arranged "back to back", and the outlet pipes are also arranged "back to back", the temperature gradient on the fin group between the inlet pipe with a higher temperature and the outlet pipe with the lowest temperature is the smallest, and the heat conduction intensity is the lowest. The "subcooling depth" of the condensate at the condenser outlet is further deepened, thereby further improving the refrigerating capacity of the evaporator.

[0188] This embodiment uses the axial flow fan 9 on the side outlet of the current situation air conditioning main unit, achieving a subversive technological breakthrough:

[0189] (1) On the air circuit side, an air flow vortex chamber is arranged on the air circuit side of the external heat exchanger of the air conditioning main unit, the spatial relationship between the air inlet chamber, the negative pressure chamber 6 and the air exhaust chamber 7 is adjusted, and the spatial relationship between the compressor chamber 8 and the air exhaust chamber 7 is adjusted. The vertical air exhaust chamber 7 in the prior art is cancelled, reducing the longitudinal depth of the main unit and further promoting the complementary structure design of the air inlet chamber, the negative pressure chamber 6 and the air exhaust chamber 7, and the complementary structure design of the compressor chamber 8 and the air exhaust chamber 7;

[0190] (2) On the fluorine circuit side, by arranging the refrigerant cross-over pipeline 12 connecting the flat fin tube heat exchangers 1 on both sides of the V shape, and setting the liquid collecting lotus head 2 and the header manifold 3 far apart from each other, and the back-to-back structure design of the subcooling sections of the refrigerant branches 11 on the fin tube heat exchanger 1 adjacent to the header manifold 3, the number of the lotus head header manifolds 3 is reduced;

[0191] Through the above-mentioned subversive innovations on the air circuit side and the fluorine circuit side, this embodiment simplifies the structure of the external heat exchanger of the air conditioning main unit, improves the uniformity of the operation of distributing the refrigerating liquid (as the evaporator) and distributing the refrigerant gas (as the condenser), and improves the subcooling degree of the condensate when used as the condenser and the superheat degree of the steam when used as the evaporator, thereby improving the energy efficiency ratio of the refrigeration air conditioning system and realizing the intensive design of the air conditioning main unit structure and the high-efficiency operation under heavy load.

[0192] Embodiment 5

[0193] As Figures 17 - 21 shown, the fin tube heat exchanger assembly of this embodiment includes a fin tube heat exchanger 1, 1 liquid collecting lotus head 2 and 1 header manifold 3;

[0194] The fin tube heat exchanger 1 can be a single-row tube, double-row tube or triple-row tube fin tube heat exchanger 1;

[0195] The finned tube heat exchanger 1 includes a number of refrigerant branches 11; the liquid fluorine interfaces of each refrigerant branch 11 are connected to the liquid-gas separating lotus head 2, and the gaseous fluorine interfaces are connected to the gas separating pipe 3; the liquid-gas separating lotus head 2 and the gas separating pipe 3 are arranged at the same side end plate 13 of the finned tube heat exchanger 1;

[0196] The refrigerant liquid pipes 14 of 2 refrigerant branches 11 that are connected to the liquid-gas separating lotus head 2 are arranged adjacent to each other on the same group of fin plates of the same row of the finned tube heat exchanger 1.

[0197] Two adjacent refrigerant branches 11 form a refrigerant pipeline module unit 16, and the 2 refrigerant liquid pipes 14 in the refrigerant pipeline module unit 16 are arranged adjacent to each other on the same group of fin plates of the same row of the finned tube heat exchanger 1; or, the 2 refrigerant liquid pipes 14 of 2 adjacent refrigerant pipeline module units 16 are arranged adjacent to each other on the same group of fin plates of the same row of the finned tube heat exchanger 1.

[0198] The refrigerant gas pipes 15 connected to the gaseous fluorine interfaces of 2 adjacent refrigerant pipeline module units 16 are arranged adjacent to each other on the same group of fin plates of the same row of the finned tube heat exchanger 1; or, the 2 refrigerant gas pipes 15 of the refrigerant pipeline module unit 16 are arranged adjacent to each other on the same group of fin plates of the same row of the finned tube heat exchanger 1.

[0199] The fluorine pipeline structure of the finned tube heat exchanger assembly in this embodiment is characterized in that:

[0200] (1) The finned tube heat exchanger 1 adopts a single-piece flat double-row (or triple-row) finned tube, or an L-shaped double-row (or triple-row) finned tube formed by rolling the flat finned tube heat exchanger 1, and the liquid-gas separating lotus head 2 and the gas separating pipe 3 are arranged adjacent to each other on the same side end plate 13 of the finned tube heat exchanger 1;

[0201] (2) The finned tube heat exchanger 1 adopted is composed of a number of refrigerant branches 11; the liquid fluorine interfaces of the refrigerant liquid pipes 14 of each refrigerant branch 11 are connected to the liquid-gas separating lotus head 2, and the gaseous fluorine interfaces of the refrigerant gas pipes 15 are connected to the gas separating pipe 3;

[0202] (3) Two adjacent refrigerant branches 11 form a refrigerant pipeline module unit 16, and the pipelines (i.e., the refrigerant liquid pipes 14) connected to the liquid fluorine interfaces of the two refrigerant branches 11 in the refrigerant pipeline module unit 16 are arranged "back to back", and the pipelines (i.e., the refrigerant gas pipes 15) connected to the gaseous fluorine interfaces are arranged far apart;

[0203] (4) The pipelines (i.e., the refrigerant gas pipes 15) connected to the gaseous fluorine interfaces of 2 adjacent refrigerant pipeline module units 16 are arranged adjacent to each other.

[0204] This embodiment discloses an air-conditioning main unit, which includes a housing 5, a negative pressure chamber 6, an exhaust chamber 7, a compressor chamber 8, a finned tube heat exchanger assembly of this embodiment 5, and a fan 9;

[0205] The compressor chamber 8 and the exhaust chamber 7 are arranged side by side on the outside of the same first side plate 54 of the negative pressure chamber 6.

[0206] The air outlet 71 of the exhaust chamber 7 is arranged on the third back plate 54 of the exhaust chamber, which is in the opposite direction to the main air inlet 101 of the air inlet chamber 10 of the housing 5.

[0207] The opposite direction setting means that the air outlet 71 and the main air inlet 101 face different directions. The main air inlet 101 is arranged on the long side of the housing 5, and the air outlet 71 is arranged on the short side of the housing 5.

[0208] The suction port direction of the fan 9 is orthogonally arranged or nearly orthogonally arranged with the main air outlet direction of the finned tube heat exchanger assembly, constructing an air flow vortex chamber between the air outlet of the finned tube heat exchanger assembly and the suction port of the fan 9 in the negative pressure chamber 6;

[0209] In the exhaust chamber 7, the fan 9 is arranged at one end close to its air outlet 71; the air outlet of the fan 9 is directly opposite to the air outlet 71 of the exhaust chamber 7; the air outlet 71 of the exhaust chamber 7 is a vertical strip-shaped air outlet;

[0210] The fan 9 is a centrifugal fan; preferably, a backward centrifugal fan is adopted; the area of the exhaust surface on the outer periphery of the fan impeller is 2 to 8 times the area of the suction port of the fan 9.

[0211] The air-conditioning main unit of this embodiment is provided with 3 vertically arranged fans 9.

[0212] The finned tube heat exchanger assembly is arranged in the air inlet chamber 10 of the housing 5 and forms a certain angle α with the main air inlet surface of the air inlet chamber 10 of the housing. The angle α is an acute angle. A more preferable angle α is 15° - 70°.

[0213] The air-conditioning main unit of this embodiment is characterized in its air path structure as follows:

[0214] ① The air inlet chamber of the external heat exchanger of the air-conditioning main unit and the negative pressure chamber 6 are connected in series, and then connected in series with the exhaust chamber 7 through the fan 9. The air inlet chamber, the negative pressure chamber 6, and the exhaust chamber 7 are arranged in sequence; in the exhaust chamber 7, the circumferential surface of the impeller of the backward centrifugal fan 9 faces the air outlet of the exhaust chamber 7; on the outside of the exhaust chamber 7 facing away from the air outlet, the compressor chamber 8 is arranged.

[0215] ② In this embodiment, the compressor chamber 8 and the centrifugal fan 9 chamber are arranged at the rear and side by side, greatly reducing or even zeroing the longitudinal exhaust chamber 7 outside the fan 9, thereby greatly reducing the size, structure, and volume of the air-conditioning main unit;

[0216] ③In this embodiment, by setting up an air flow vortex chamber, adjusting the spatial relationship between the air inlet chamber negative pressure chamber 6 and the air exhaust chamber 7, and adjusting the spatial relationship between the compressor chamber 8 and the air exhaust chamber 7, the vertical air exhaust chamber 7 of the air conditioner main unit in the background art is removed, reducing the longitudinal depth of the air conditioner main unit and further promoting the complementary design of the structures of the compressor chamber 8 and the air exhaust chamber 7, making it possible to have a wall-mounted air conditioner main unit with a compact structure.

[0217] When the air conditioner main unit of this embodiment operates in refrigeration mode, the high-temperature and high-pressure refrigerant gas discharged by the compressor 4 is sent into the refrigerant pipeline module unit 16 in the condenser, into two pipelines connected by two relatively distant refrigerant gas interfaces. One path of the high-temperature and high-pressure refrigerant gas advances forward along the pipeline and runs downward through each pipeline in turn; the other path of the high-temperature and high-pressure refrigerant gas advances forward along the pipeline and runs upward through each pipe in turn; finally, it flows into the pipeline at the end of the condenser arranged adjacent to it, converges at the lotus head, and is discharged from the condenser.

[0218] At present, at the end (subcooling section) of each fluorine circuit branch of the finned tube condenser, the pipeline is also connected to the inlet pipeline of the high-temperature refrigerant gas of the next branch through fins, passively receiving the heat conducted through the fin heat bridge from the high-temperature and high-pressure refrigerant gas in the inlet pipeline of the next adjacent branch. Moreover, the length of the fin heat bridge is very short and the conduction temperature difference is extremely large (up to more than 50 °C), resulting in the subcooled condensate both subcooling and releasing heat to the ventilation air flow through the fin group and being heated by the high-temperature and high-pressure refrigerant gas in the adjacent branch through the fin heat bridge, making it difficult to deeply implement the "subcooling operation".

[0219] In this embodiment, since the pipelines (i.e., the refrigerant liquid pipes 14) connected by the liquid interfaces of the two refrigerant branches 11 in the refrigerant pipeline module unit 16 are arranged in a "back-to-back" manner, that is, when used as a condenser, the end condensate pipelines (i.e., the refrigerant liquid pipes 14) of the two refrigerant branches 11 are arranged "back-to-back"; moreover, the high-temperature and high-pressure refrigerant gas inlet pipelines (i.e., the refrigerant gas pipes 15) connected by the gas interfaces of two adjacent refrigerant pipeline module units 16 are also arranged "back-to-back"; in summary, the fin length between the high-temperature inlet pipe and the liquid outlet pipe with the lowest temperature on each refrigerant branch 11 is relatively large, the temperature gradient on the fin group is relatively small, and the heat conduction intensity is relatively low, further deepening the "subcooling depth" of the condensate at the condenser outlet, thereby further improving the refrigeration capacity of the evaporator.

[0220] When the air conditioner main unit of this embodiment is operating, in the air duct of the external heat exchanger, ambient air is drawn in by the negative pressure of the fan 9 through the narrow air duct of the finned tube heat exchanger 1 and the negative pressure chamber, obtaining a speed of about 4 m / s and a dynamic pressure head; the main air flow at the outlet of the external heat exchanger further increases its speed to about 6 m / s, and rushes inertially towards the opposite air flow vortex chamber wall plate, where it is blocked, decelerated, and reflected by the opposite wall plate, and directly drives the suction port of the fan 9; especially the inertial air flow between the adjacent suction ports of the fan 9 in the vertical direction, between the high-position suction port of the fan 9 and the top plate of the air flow vortex chamber (close to the main unit cover plate), and between the low-position suction port of the fan 9 and the bottom plate of the air flow vortex chamber (close to the main unit chassis), after being blocked, decelerated, and reflected by the opposite wall plate, flows towards the suction port area of the fan 9 adjacent to the opposite wall plate, realizing the deceleration, pressure increase, reorganization, and redistribution of the heat exchange air flow in the air flow vortex chamber, and improving the uniformity and stability of the air flow entering the suction port of the fan 9;

[0221] When the heat exchanger of the air conditioner main unit of this embodiment is operating, one side of the finned tube heat exchanger 1 is for air inlet and the opposite side is for air exhaust. The air flow lines entering the fin gaps intersect the plane where the fins are located at an obtuse angle. The fins "obliquely cut" the air flow lines with a speed of about 4 m / s, and it is the huge number of fin planer knives on the finned tube heat exchanger 1 that successively plane the incoming air flow, and then each "planed flower-shaped" air flow cut off is stuffed into a corresponding fin gap to implement "low-speed air distribution" of about 1.5 m / s for the fin gaps; when the air flow lines after heat exchange leave the fin gaps, they are once again "obliquely cut" by the long sides of the fins, turn and then enter the suction port of the centrifugal fan 9; the heat exchange air flow is pressurized by the centrifugal fan 9 and discharged into the exhaust chamber 7 and then shot into the ambient air at high speed for diffusion and dilution.

[0222] The advantage of this embodiment is that by simply swapping the inlets and outlets of about half of the refrigerant branches 11 on the finned tube heat exchanger 1, the fin length between the high-temperature inlet pipes (i.e., refrigerant gas pipes 15) and the liquid outlet pipes with the lowest temperature (i.e., refrigerant liquid pipes 14) on each refrigerant branch 11 is increased, the temperature gradient on the fin group becomes smaller, the heat conduction intensity along the fin direction is reduced, and the "subcooling depth" of the condensate at the condenser outlet is further deepened, thereby further enhancing the refrigerating capacity of the evaporator.

[0223] Embodiment 6

[0224] As Figure 22 shown, the finned tube heat exchanger assembly of this embodiment includes several flat-plate finned tube heat exchangers 1, a liquid distribution and collection lotus head 2, and a gas collection and distribution pipe 3;

[0225] The finned tube heat exchanger 1 can be a single-row tube, double-row tube, or triple-row tube finned tube heat exchanger 1;

[0226] The flat finned tube heat exchanger 1 includes several refrigerant branches 11; the refrigerant branches 11 between different flat finned tube heat exchangers 1 are connected in series through refrigerant bypass pipelines 12; the refrigerant branch 11 is connected to the liquid distribution and collection lotus head 2 and the gas collection and distribution pipe 3 to form a finned tube heat exchanger assembly.

[0227] The liquid distribution and collection lotus head 2 and the gas collection and distribution pipe 3 are respectively arranged at the end plates 13 of different flat finned tube heat exchangers 1.

[0228] The refrigerant branches 11 between adjacent flat finned tube heat exchangers 1 are connected through the refrigerant bypass pipeline 12 to communicate the refrigerant branches 11. The superheat heat exchange section, phase change heat exchange section, and subcooling heat exchange section of any refrigerant branch 11 between the gas collection and distribution pipe 3 and the liquid distribution and collection lotus head 2 are distributed in each flat finned tube heat exchanger 1; or, any refrigerant branch 11 between the liquid distribution and collection lotus head 2 and the gas collection and distribution pipe 3 is arranged in sections in each flat finned tube heat exchanger 1.

[0229] In the condenser of this embodiment, since the refrigerant branch pipelines in each flat finned tube heat exchanger 1 adjacent to the gas collection and distribution pipe 3 are arranged in a "back-to-back" manner in pairs, the condensation heat release section pipelines of two adjacent refrigerant branches 11 in the middle flat finned tube heat exchanger 1 of the condenser are arranged "back-to-back", and the condensate outlet pipes (i.e., the refrigerant liquid pipes 14) of two adjacent refrigerant branches in the flat finned tube heat exchanger 1 at the end of the condenser are also arranged "back-to-back". While giving full play to the advantage of the finned tube heat exchanger in increasing the heat exchange area of the refrigerant pipeline, it eliminates the problem that usually exists in the current finned tube condenser, that is, the high-temperature and high-pressure refrigerant gas conducts heat through the fin heat bridge to the condensate in the copper pipe in the subcooling heat release stage, hindering the deep subcooling of the condensate and reducing the refrigeration capacity of the evaporator; moreover, in the flat finned tube heat exchanger 1 adjacent to the liquid distribution and collection lotus head 2 and used as the subcooling heat release section, the temperature gradient on the fin group between the inlet pipe with a slightly higher temperature and the outlet pipe with the lowest temperature of each refrigerant branch 11 is the smallest, and the heat conduction intensity is the lowest, further deepening the "subcooling depth" of the condensate at the outlet of the condenser, thereby further improving the refrigeration capacity of the evaporator.

[0230] The refrigerant liquid pipes 14 connecting the two refrigerant branches 11 to the liquid distribution and collection lotus head 2 are arranged adjacent to each other on the same set of fin plates of the same row of finned tube heat exchangers 1.

[0231] The refrigerant gas pipes 15 connecting the two refrigerant branches 11 to the gas collection and distribution pipe 3 are arranged far from each other on the same set of fin plates of the same row of finned tube heat exchangers 1.

[0232] A refrigerant cross - over pipeline 12 is set, and the structure of the fin - tube heat exchanger assembly with ultra - high heat - transfer efficiency, where the liquid - distributing and liquid - collecting lotus head 2 and the gas - distributing and gas - collecting pipe 3 are set far apart, is composed of a copper - tube M - shape, which is formed by combining the refrigerant branches 11 of 4 flat - type fin - tube heat exchangers 1; each branch has 4×3 copper tubes; the refrigerant - branch pipelines in the flat - type fin - tube heat exchanger adjacent to the gas - distributing and gas - collecting pipe 3 are arranged back - to - back.

[0233] Embodiment 7

[0234] As Figure 23 shown, a fin - tube heat exchanger assembly of this embodiment includes a fin - tube heat exchanger 1, 1 liquid - distributing and liquid - collecting lotus head 2, and 1 gas - distributing and gas - collecting pipe 3;

[0235] The fin - tube heat exchanger 1 is an L - type double - row fin - tube heat exchanger formed by rolling a flat - type fin - tube heat exchanger 1;

[0236] The fin - tube heat exchanger 1 includes several refrigerant branches 11; the liquid - phase interfaces of the fluorine circuits of each refrigerant branch 11 are connected to the liquid - distributing and liquid - collecting lotus head 2, and the gas - phase interfaces of the fluorine circuits are connected to the gas - distributing and gas - collecting pipe 3; the liquid - distributing and liquid - collecting lotus head 2 and the gas - distributing and gas - collecting pipe 3 are arranged at the same side end - plate 13 of the fin - tube heat exchanger 1; the refrigerant liquid pipes 14 connecting the liquid - distributing and liquid - collecting lotus head 2 of 2 refrigerant branches 11 are arranged adjacent to each other on the same set of fin - plates of the same row of the fin - tube heat exchanger 1.

[0237] Two adjacent refrigerant branches 11 form a refrigerant pipeline module unit 16, and the 2 refrigerant liquid pipes 14 in the refrigerant pipeline module unit 16 are arranged adjacent to each other on the same set of fin - plates of the same row of the fin - tube heat exchanger 1; or, the 2 refrigerant liquid pipes 14 of 2 adjacent refrigerant pipeline module units 16 are arranged adjacent to each other on the same set of fin - plates of the same row of the fin - tube heat exchanger 1.

[0238] The refrigerant gas pipes 15 connected to the gas - phase interfaces of 2 adjacent refrigerant pipeline module units 16 are arranged adjacent to each other on the same set of fin - plates of the same row of the fin - tube heat exchanger 1; or, the 2 refrigerant gas pipes 15 of the refrigerant pipeline module unit 16 are arranged adjacent to each other on the same set of fin - plates of the same row of the fin - tube heat exchanger 1.

[0239] The fluorine - circuit structural feature of the fin - tube heat exchanger assembly of this embodiment is as follows:

[0240] (1) The fin - tube heat exchanger 1 is an L - type double - row fin - tube heat exchanger formed by rolling a flat - type fin - tube heat exchanger 1, and the liquid - distributing and liquid - collecting lotus head 2 and the gas - distributing and gas - collecting pipe 3 are arranged adjacent to each other on the same side end - plate 13 of the fin - tube heat exchanger 1;

[0241] (2) The finned tube heat exchanger 1 adopted is composed of a number of refrigerant branches 11; the liquid fluorine interfaces of each refrigerant branch 11 are connected to the liquid-gas separating lotus head 2, and the gaseous fluorine interfaces are connected to the gas collecting and distributing pipe 3;

[0242] (3) Two adjacent refrigerant branches 11 form a refrigerant pipeline module unit 16. The pipelines connected to the liquid fluorine interfaces of the two branches of the refrigerant pipeline module unit 16 are arranged "back to back", and the pipelines connected to the gaseous fluorine interfaces are also arranged "back to back";

[0243] As Figure 24 shown, this embodiment discloses an air-conditioning main unit, which includes a housing 5, a negative pressure chamber 6, an exhaust chamber 7, a compressor chamber 8, the finned tube heat exchanger assembly of this embodiment, and a fan 9;

[0244] The negative pressure chamber 6 and the exhaust chamber 7 are arranged side by side; the exhaust port 71 of the exhaust chamber 7 is arranged side by side with the main air inlet 101 of the air inlet chamber of the housing 5, that is, the exhaust port 71 of the exhaust chamber 7 is arranged on the same side as the main air inlet 101 of the air inlet chamber of the housing 5.

[0245] The suction port direction of the fan 9 is orthogonally arranged or nearly orthogonally arranged with the main air outlet direction of the finned tube heat exchanger assembly, constructing an air flow vortex chamber between the air outlet of the finned tube heat exchanger assembly in the negative pressure chamber 6 and the suction port of the fan 9;

[0246] The fan 9 in the exhaust chamber 7 is arranged at one end far from its exhaust port 71; the air outlet of the fan 9 faces the exhaust port 71 of the exhaust chamber 7; the exhaust port 71 of the exhaust chamber 7 is a vertical strip-shaped exhaust port;

[0247] The compressor chamber 8 is arranged outside the first back plate 55 of the negative pressure chamber 6 and the exhaust chamber 7.

[0248] The fan 9 is a centrifugal fan; preferably, a backward centrifugal fan is adopted; the area of the exhaust surface on the outer periphery of the impeller of the fan 9 is 2 to 8 times the area of the suction port of the fan 9.

[0249] This embodiment of the air-conditioning main unit is provided with 2 vertically arranged fans 9.

[0250] The finned tube heat exchanger assembly is arranged in the air inlet chamber of the housing 5; one side of the finned tube heat exchanger assembly is close to the main air inlet 101;

[0251] The air inlet chamber of the housing 5 is also provided with a second air inlet 52; a throttle panel 56 is provided at the second air inlet 52; the throttle panel 56 is provided with areas with different throttle resistances;

[0252] As Figure 19As shown in the figure, in area A, which is closest to the air inlet of the fan 9 and has the smallest air flow turning angle, the permeability of the throttle panel 56 is 20%-40%, and the throttling resistance is the greatest. As the distance between the heat exchange area on the finned tube heat exchanger and the air inlet of the fan 9 gradually increases and the air flow turning angle increases, the permeability of the corresponding throttle panel 56 of the corresponding section increases accordingly. The permeability of the throttle panel 56 corresponding to areas B, C, and D is increased to 40%-60%, 60%-70%, and 70%-80% respectively.

[0253] When the main unit of the air conditioner in this embodiment operates in refrigeration mode, the high-temperature and high-pressure refrigerant gas discharged from the compressor is sent into the refrigerant pipeline module unit 16 in the condenser. In the pipelines connected to the two adjacent refrigerant gas interfaces in the same single-row finned tube heat exchanger 1, one path of high-temperature and high-pressure refrigerant gas advances forward along the pipeline, and runs downward through each pipeline in turn. Then it enters another single-row finned tube heat exchanger 1 and runs upward through each pipeline in turn. Another path of high-temperature and high-pressure refrigerant gas advances forward along the pipeline and runs upward through each tube in turn. Then it enters another single-row finned tube heat exchanger 1 and runs downward through each pipeline in turn. Finally, it flows into the condenser end pipeline arranged adjacent to each other in the refrigerant pipeline module unit 16, is discharged from the condenser in the same direction, and enters the liquid collection lotus head 2 for collection.

[0254] In this embodiment, since the pipelines connected to the liquid interfaces and gas interfaces of the two refrigerant branches 11 in the refrigerant pipeline module unit 16 of the double-row finned tube heat exchanger 1 are both arranged in a "back-to-back" manner in the same single-row finned tube heat exchanger 1, that is, when used as a condenser, the end refrigerant liquid pipes 14 of the two refrigerant branches 11 are arranged "back-to-back". Moreover, the refrigerant gas pipes 15 of the two refrigerant branches 11 of the refrigerant pipeline module unit 16 are arranged "back-to-back" in another single-row finned tube heat exchanger 1 where the fin heat bridge is disconnected. In short, the high-temperature inlet pipes and low-temperature outlet pipes on the two refrigerant branches 11 in each refrigerant pipeline module unit 16 are arranged "back-to-back" on different single-row finned tube heat exchangers 1, weakening the conduction of refrigerant heat along the fins across the copper tubes and strengthening the heat exchange between the refrigerant and the ventilation air flow. The fin heat bridge between the high-temperature inlet pipe and the lowest-temperature outlet pipe on the two refrigerant branches 11 in each refrigerant pipeline module unit 16 is disconnected, and the "subcooling depth" of the condensate at the outlets of the two refrigerant branches 11 is further deepened, thereby further increasing the refrigeration capacity of the system evaporator.

[0255] Embodiment 8

[0256] As Figure 25 shown, a copper tube M-type finned tube heat exchanger assembly includes 4 flat-plate finned tube heat exchangers 1, a liquid collection lotus head 2, and a gas collection and distribution pipe 3.

[0257] The fin-tube heat exchanger 1 may be a single-row, double-row or triple-row fin-tube heat exchanger 1;

[0258] The flat plate fin tube heat exchanger 1 comprises a plurality of refrigerant branches 11; the refrigerant branches 11 between different flat plate fin tube heat exchangers 1 are connected in series via a refrigerant bridge pipe 12; the refrigerant branches 11 are connected to the liquid collecting lotus head 2 and the gas collecting pipe 3 to form a fin tube heat exchanger assembly.

[0259] The liquid collecting lotus head 2 and the gas collecting and distributing pipe 3 are respectively arranged at the end plates 13 of different flat plate fin-tube heat exchangers 1 .

[0260] Adjacent flat plate fin tube heat exchangers 1 are connected to the refrigerant branch 11 through the refrigerant bridge pipe 12, and the superheating heat exchange section, phase change heat exchange section, and subcooling heat exchange section of any refrigerant branch 11 from the gas collecting and distributing pipe 3 to the liquid collecting lotus head 2 are distributed in each flat plate fin tube heat exchanger 1;

[0261] Any refrigerant branch 11 from the liquid collecting lotus head 2 to the gas collecting and distributing pipe 3 is arranged in sections in each flat plate fin tube heat exchanger 1 .

[0262] The refrigerant liquid pipes 14 of the two refrigerant branches 11 communicating with the liquid distribution lotus heads 2 are arranged adjacent to each other on the same group of fin plates of the same row of fin-tube heat exchangers 1 .

[0263] The total length of the refrigerant pipelines of any refrigerant branch 11 from the liquid distribution lotus head 2 to the gas distribution pipe 3 is equal or substantially equal.

[0264] The fin tube heat exchanger assembly of this embodiment is provided with a refrigerant bridge pipe 12, and the liquid distribution lotus head 2 and the gas distribution pipe 3 are arranged far apart, which has an ultra-high heat exchange efficiency. The structure of the fin tube heat exchanger assembly is a copper tube M-shaped structure, which is composed of four flat-plate fin tube heat exchangers 1. Each refrigerant branch 11 uses a number of straight tube refrigerant pipes, and the refrigerant branches 11 are evenly arranged on the first flat-plate fin tube heat exchanger 1, complementary arranged on the second / third flat-plate fin tube heat exchangers 1, and the refrigerant liquid pipe 14 connected to the liquid distribution lotus head 2 on the fourth flat-plate fin tube heat exchanger 1 is arranged "back to back".

[0265] In this embodiment, since "the refrigerant branch 11 is evenly arranged on the first flat plate fin-tube heat exchanger 1 and complementarily arranged on the second / third flat plate fin-tube heat exchangers 1", the heat load of the second / third flat plate fin-tube heat exchangers 1 is evenly arranged; and since "the refrigerant liquid pipe 14 is arranged back to back on the fourth flat plate fin-tube heat exchanger 1, the refrigerant branch 11 on the fourth flat plate fin-tube heat exchanger 1 at the end of the condenser is arranged "back to back" during operation, and the refrigerant liquid pipe 14 connected to the distribution liquid lotus head 2 is also arranged "back to back", the temperature gradient on the fin group between the higher temperature inlet pipe and the lowest temperature outlet pipe is the smallest, the heat conduction intensity is the lowest, and the "subcooling depth" of the condensate at the condenser outlet is further deepened, thereby further improving the evaporator cooling capacity.

[0266] Example 9

[0267] The fundamental change in the application scenarios of air conditioner hosts now calls for disruptive innovation in the structure of the air conditioner host and the spatial relationship between the air conditioner host and the equipment platform:

[0268] First, driven by the housing and construction department's policy that "equipment platform area is not included in the building's gross floor area", the independent equipment platform with good accessibility of the "all-in-one" air-conditioning host with one-to-many multi-connections has been effectively implemented, and the potential of multi-connections to reduce noise radiation range and simple and elegant indoor and outdoor decoration has been fully explored, replacing one-to-one room air conditioners (split air conditioners) and becoming the mainstream product in the air-conditioning market;

[0269] Secondly, the traditional multi-split air-conditioning host with axial fan side outlet is hung on the outer wall of the building to enter the interior of the equipment platform. The inlet and outlet air paths of the external heat exchanger face unprecedentedly stringent spatial constraints of the equipment platform, namely "floor below, ceiling above, wall behind, and shutters in front". The side-outlet air-conditioning host faces the shutters, the exhaust static pressure increases, the air volume decreases, and some of the reduced air volume short-circuits back, causing serious degradation of air conditioning performance.

[0270] In response to the above-mentioned air-conditioning application scenario problems and innovation opportunities, an air-conditioning host device platform in this embodiment is constructed into a high-quality device platform with structural coupling, air path coupling, and energy coupling between the air-conditioning host and the device platform facade through innovations in the air-conditioning host body structure and the spatial relationship between the air-conditioning host and the device platform facade.

[0271] The equipment platform of this embodiment is provided with the air-conditioning host of embodiment 2.

[0272] like Figures 26 - 27As shown in the figure, in this embodiment, an air-conditioning host equipment platform 36 is usually set on the north side of the building. Preferably, it is set on the north side of the public toilet to reduce the occupation of the effective overhanging surface resources of the building, and is connected to the north living balcony to fundamentally solve the accessibility of the equipment platform 36; the air-conditioning host is provided with vertical strip-shaped air vents, and the vertical strip-shaped air outlets correspond to the vertical strip-shaped metal meshes 41 reserved on the outer facade of the equipment platform 36; a decorative outer facade of the equipment platform 36 can be set. Narrow strip-shaped decorative boards can be arranged in a staggered manner front and back, leaving a longitudinal gap between the boards as the air inlet; the decorative structure 40 of the outer facade can be a group of metal columns, can be a shutter, or can be a garden door, a classical entrance door, a landscape painting, etc.; in this embodiment, the shutter decorative structure 40 is adopted.

[0273] When the air-conditioning host in this embodiment operates, the fresh air is inhaled into the air inlet of the external heat exchanger of the air-conditioning host, creating a slightly negative pressure state in the entire space of the equipment platform 36, pulling the ambient air to pass through the air inlet area on the external shutter (or other forms of ventilated outer facade) of the outer facade in a large area at a low speed and entering the internal space of the equipment platform 36. The internal space of the equipment platform 36 and the air inlet duct of the external heat exchanger are combined into one; while the small-area metal mesh 41 on the side of the outer facade corresponding to the vertical strip-shaped air outlet area of the air-conditioning host constitutes the exhaust area; the air inlet area and the exhaust area are separated from each other, blocking the possibility of the exhaust air of the air-conditioning host flowing back and short-circuiting; and, measured with the outer facade of the equipment platform 36 as the reference plane, in this embodiment, the external heat exchanger of the air-conditioning host is externally connected with a closed rear guide section. The area of the air outlet of the metal mesh 41 on the outer facade is very small, significantly smaller than the area of the external shutter of the air inlet area (less than 1 / 10); the air inlet air flow in the shutter area has a very low speed and very small resistance when passing through the shutter, while the exhaust air flow shoots into the ambient air at a small angle after passing through the metal mesh 41 on the side of the shutter, with a high speed, a long range, and a good diffusion and dilution effect; the thermal performance of the air-conditioning host on the equipment platform 36 in this embodiment has not decreased compared with the laboratory data, and the task of being a "heat transporter" is completed with high quality and high efficiency;

[0274] This embodiment not only eliminates the obstruction of the shutter of the equipment platform 36 to the exhaust of the external heat exchanger of the classic axial flow fan 9, realizes the integration of the internal space of the equipment platform 36 and the air inlet duct of the external heat exchanger, effectively penetrates the air path of the external heat exchanger, and ensures the thermal performance of the air-conditioning host, but also maintains the decoration of the outer facade in the form of shutters, etc., realizing the perfect unity of the decoration of the outer facade of the equipment platform 36, the visual effect of the building's outer facade and the excellent thermal performance of the air-conditioning host.

[0275] The advantages of the equipment platform 36 in this embodiment are as follows:

[0276] (1) Construct an efficient air path system for the external heat exchanger of the air-conditioning host to penetrate the outer facade of the equipment platform 36

[0277] The vertical strip-shaped air outlet design with a rearward exhaust section close to the side of the outer facade of the equipment platform 36 in this embodiment can greatly reduce the width of the air outlet, reduce the occupation of the decorative louvers commonly used on the outer facade, especially reduce the occupation of the effective overhanging surface of the building. It not only maintains the decoration of the louvered building outer facade but also effectively improves the range and diffusion dilution effect of the exhaust air from the external heat exchanger of the air-conditioning main unit passing through the outer facade of the equipment platform 36 into the ambient atmosphere.

[0278] This embodiment eliminates the obstruction of the louver to the exhaust air of the external heat exchanger of the classic axial-flow fan 9 side-outlet air-conditioning main unit, combines the internal space of the equipment platform 36 with the air inlet duct of the external heat exchanger, effectively penetrates the air path of the external heat exchanger, ensures the thermal performance of the air-conditioning main unit, and maintains the decoration of the louver outer facade. It realizes the perfect unity of the decoration of the outer facade of the equipment platform 36, the visual effect of the building outer facade, and the excellent thermal performance of the air-conditioning main unit.

[0279] (2) Improve the power density of the equipment platform and reduce the land occupation of the equipment platform

[0280] The air-conditioning main unit of this embodiment adopts new technologies such as setting the air outlet direction of the heat exchanger orthogonal to the suction port direction of the fan 9, setting the air inlet and outlet of the air-conditioning main unit far apart, connecting the finned tube heat exchanger 1 through the refrigerant cross-over pipeline 12, setting the distributed liquid lotus head 2 far from the distributed gas pipe 3, and setting the subcooling section on the flat finned tube of the adjacent lotus head back to back. It also raises the height of the air-conditioning main unit to develop the idle space at the top of the equipment platform 36, effectively reduces the floor area of the ineffective and low-efficiency space on the equipment platform 36, greatly improves the average cooling and heating power density and energy efficiency ratio of the equipment platform 36, and saves a large amount of the area of the equipment platform 36 under the same cooling and heating load.

[0281] (3) Facilitate the detection and maintenance of the air-conditioning main unit

[0282] The equipment platform 36 adopted in this embodiment is connected to the north living balcony, which solves the accessibility of the equipment platform 36.

[0283] The air-conditioning main unit adopted in this embodiment centrally arranges the fluorine circuit and electrical components such as the compressor, four-way valve, expansion valve, and electrical box into the compressor chamber 8 juxtaposed with the exhaust chamber 7. All the fluorine circuit and air path components of the air-conditioning main unit are set in a cavity with only one-layer shell that can be disassembled. The air-conditioning main unit is also set on the accessible equipment platform 36, which fundamentally solves the convenience problem of the operation, maintenance management, and fault repair of the air-conditioning main unit.

[0284] Embodiment 10

[0285] As Figures 28 - 32As shown in the figure, in this embodiment, a device platform constructs a commercial air-conditioning main body with subversive features and a high-quality commercial air-conditioning main body device platform that realizes structural coupling, air duct coupling, and energy coupling between the commercial air-conditioning main body and the outer facade of the device platform through the innovation of the structure of the air-conditioning main body and the innovation of the spatial relationship between the air-conditioning main body and the outer facade of the device platform.

[0286] A combined commercial air-conditioning main body in this embodiment is composed of modular assemblies. The modules include a compressor cavity 31 provided with a compressor 4, a finned tube heat exchanger assembly outer heat exchanger assembly cavity 33, a vertical exhaust cavity 32, and a longitudinal exhaust cavity 34 communicated with the vertical exhaust cavity 32; the longitudinal exhaust cavity 34 is arranged below the outer heat exchanger assembly cavity 33 and is fixedly connected to the bottom plate of the vertical exhaust cavity 32; the compressor cavity 31 is arranged on the back plate of the longitudinal exhaust cavity 34 and is communicated with the outer heat exchanger assembly cavity 33 for the fluorine circuit and the electric circuit; the air outlet 71 of the longitudinal exhaust cavity 34 faces the same direction as the main air inlet 101 of the finned tube heat exchanger assembly.

[0287] The horizontal interface size of the longitudinal exhaust cavity 34 is greater than or equal to the horizontal cross-sectional size of the outer heat exchanger assembly cavity 33.

[0288] The compressor cavity 31 is arranged on the back plate of the longitudinal exhaust cavity 34.

[0289] Both the bottom of the longitudinal exhaust cavity 34 and the compressor cavity 31 are provided with bases 35.

[0290] The size of the module is designed to meet the size requirements for entering a common elevator car and the car door.

[0291] On the basis of continuing to inherit the design technologies such as the zigzag outer heat exchanger assembly cavity 33, the main air inlet 101 and the air outlet 71 being arranged on the same side and vertically, expanding the top space of the device platform 36, and constructing a decorative structure 40 with low resistance through the outer facade of the device platform in the commercial air-conditioning main body, aiming at the problems in the background technology, focusing on the two major scenario-based and technological practical problems of using a common elevator for vertical transportation of the air-conditioning main body and the operation space required for maintenance of the air-conditioning main body on the device platform 36, the commercial air-conditioning main body is decoupled and modularly designed, and the commercial air-conditioning main body is decoupled into at least three primary components such as the compressor cavity 31, the outer heat exchanger assembly cavity 33, and the longitudinal exhaust cavity 34; the size of each primary component is designed to meet the requirements of vertical transportation by a common elevator.

[0292] For the three primary components such as the compressor cavity 31, the longitudinal exhaust air cavity 34, and the external heat exchanger assembly cavity 33 in this embodiment, the technical parameters and structural dimensions are planned and balanced uniformly. They are designed and manufactured independently, transported to the site of the commercial building equipment platform in batches by elevator, and then assembled into the whole commercial air conditioner host. Finally, the fluorine circuit and the electric circuit connecting the air conditioner host and the air conditioner indoor unit 42 are connected to jointly construct a closed multi-connected refrigerant circuit.

[0293] In this embodiment, for the whole commercial host built by the three primary components including the compressor cavity 31, the longitudinal exhaust air cavity 34, and the external heat exchanger assembly cavity 33, the external heat exchanger assembly cavity 33 and the longitudinal exhaust air cavity 34 have an upper and lower two-section structure, and the compressor cavity 1 is attached to the two-section structure.

[0294] In this embodiment, for the longitudinal exhaust air cavity 34 which is the lower section of the two-section structure, its three sides extend outwards, that is, the horizontal interface dimension of the longitudinal exhaust air cavity 34 is greater than or equal to the horizontal cross-section dimension of the external heat exchanger assembly cavity 33.

[0295] Its horizontal extensions on the left and right sides expand the width of the longitudinal exhaust air cavity 34, reduce the height of the longitudinal exhaust air cavity 34 and the vertical ratio of the height of the longitudinal exhaust air cavity 34 on the outer facade of the equipment platform, and set the lower limit of the horizontal interval between adjacent hosts; its longitudinal extension section at the front side inserts forward above the anti-camber of the equipment platform 36 in the upper direction of the base 35 and docks with the pre-set exhaust air opening on the outer facade; its longitudinal extension section at the front side is connected with the horizontal extension sections on both sides to form a platform-style waistline of the air conditioner host, providing necessary operation space for operators to install, repair, maintain, and remove the external heat exchanger assembly cavity of the air conditioner host.

[0296] The secondary components of the three primary components in this embodiment are as follows:

[0297] 1. The external heat exchanger assembly cavity 33, including the finned tube heat exchanger assembly, the backward centrifugal fan 9, the vertical exhaust air cavity 32, etc.; the finned tube heat exchanger assembly is arranged on the air inlet surface of the main air inlet 101 of the external heat exchanger assembly cavity 33 and forms a heat exchanger assembly negative pressure cavity communicating with the heat exchange air path of the finned tube heat exchanger assembly with part of the shell; an air outlet is arranged on the back plate of the heat exchanger assembly negative pressure cavity, and 2 backward centrifugal fans 9 and the vertical exhaust air cavity 32 are installed at the air outlet.

[0298] 2. The longitudinal exhaust air cavity 34, including the longitudinal exhaust air cavity 33 communicating with the vertical exhaust air cavity 32 and the horizontal extension exhaust section 34, etc.; the exhaust air opening 71 of the longitudinal exhaust air cavity 34 faces the short side of the air conditioner host.

[0299] 3. The compressor cavity 31, including the compressor 4, the gas-liquid separator, the expansion valve 37, the four-way valve 38, the electric control box 39, etc.

[0300] In this embodiment, the backward centrifugal fan 9 in the cavity 33 of the after-heat exchanger assembly is the biggest constraint factor in meeting the structural design conditions of the air-conditioning main unit for elevator transportation because the outer diameter of the impeller significantly exceeds the diameter of the impeller air suction port. In this embodiment, a backward centrifugal fan 9 with low static pressure, large air volume and low noise is adopted, and the outer diameter of the impeller is greatly reduced under the condition that the diameter of the impeller air suction port is determined to reduce the constraint of the centrifugal fan on the structural design of the main unit.

[0301] On the fluorine circuit side, for the finned-tube heat exchanger assembly of the commercial air-conditioning main unit in this embodiment, the refrigerant bypass pipeline 12 is provided to connect the 4 flat finned-tube heat exchangers 1 that make up the copper-tube M-shaped finned-tube heat exchanger assembly; only one set of liquid-distributing and liquid-collecting lotus heads 2 and gas-collecting and gas-distributing pipes 3 are used to perform liquid distribution (collection) and gas collection (distribution) for the refrigerant branches 11 arranged on the 4 flat finned-tube heat exchangers of the copper-tube M-shaped finned-tube heat exchanger assembly; moreover, the liquid-distributing and liquid-collecting lotus heads 2 and the gas-collecting and gas-distributing pipes 3 are arranged on different sides, that is, far apart from each other, and are arranged on the two side edges of the two finned-tube heat exchangers 1 of the M-shaped finned-tube heat exchanger assembly.

[0302] From the perspective of the fluorine circuit structure, in this embodiment, starting from the liquid-distributing and liquid-collecting lotus head 2, through the thin-diameter liquid-distributing pipe, it is connected to the pipe orifice and pipeline corresponding to the refrigerant branch 11 on the end plate 13 of the first flat finned-tube adjacent to the side of the liquid-distributing and liquid-collecting lotus head 2, and then the corresponding pipe orifices and pipelines of the refrigerant branches 11 on the second / third flat finned-tubes are sequentially connected in a bridging manner through the refrigerant bypass pipeline 12 twice each time, and finally connected to the gas-collecting and gas-distributing pipe 3 through the pipeline; for the refrigerant branch 11 on the fourth flat finned-tube heat exchanger 1 at the end of the condenser, during operation, the condensate inlet pipes of two adjacent refrigerant branches 11 are arranged "back to back", and the outlet pipes are also arranged "back to back". The temperature gradient on the fin group between the inlet pipe with a higher temperature and the outlet pipe with the lowest temperature is the smallest, and the heat conduction intensity is the lowest, and the "subcooling depth" of the condensate at the condenser outlet is further deepened, thereby further improving the refrigerating capacity of the evaporator.

[0303] When installing the combined commercial coupled air-conditioning main unit in this embodiment, three primary components, namely the compressor cavity, the horizontal exhaust cavity, and the external heat exchanger cavity, are respectively transported to the floor where the commercial building equipment platform is located by an elevator and then horizontally transferred to the equipment platform site. At the site, they are successively assembled in the order of the horizontal exhaust cavity, the external heat exchanger cavity, and the compressor cavity. The exhaust section of the horizontal exhaust cavity is aligned with the low-position exhaust opening reserved on the external facade, and the air inlet of the external heat exchanger assembly cavity is aligned with the upper-middle decorative structure 40 on the external facade. The vertical exhaust cavity in the external heat exchanger assembly cavity is connected to the horizontal exhaust cavity, completing the internal placement of the air path of the external heat exchanger of the air-conditioning main unit and the through connection of the internal and external air paths of the equipment platform. Then, the refrigerant fluorine path between the compressor cavity and the external heat exchanger assembly cavity is connected to form the whole commercial air-conditioning main unit. After that, it is connected to the fluorine path of the air-conditioning indoor unit (or the built-in shell-and-tube heat exchanger or plate heat exchanger in the main unit) to jointly build a closed multi-connected refrigerant circuit.

[0304] The longitudinal extension section on the front side of the horizontal exhaust cavity 7 of the combined commercial coupled air-conditioning main unit in this embodiment, together with the horizontal extension sections on its two sides, is connected to form the platform-style waist circumference of the main unit, providing an important operating space for operators to install, repair, and maintain the negative pressure cavity 6 of the air-conditioning main unit.

[0305] When this embodiment is in operation, the ambient fresh air passes through the upper-middle decorative structure 40 (such as louvers) on the external facade of the equipment platform in a large area, at a low speed, and with low resistance, and then passes through the front air inlet surface and the side air supply slits on both sides of the external heat exchanger assembly cavity of the air-conditioning main unit to enter the M finned tube heat exchanger. After heat exchange, it is sucked by the centrifugal fan, pressurized, sent into the vertical exhaust cavity in the external heat exchanger assembly cavity, then turned into the bottom horizontal exhaust cavity, and finally ejected at a high speed from the exhaust port of the exhaust section extending forward of the horizontal exhaust cavity connected to the reserved exhaust opening on the docking external facade and diffused and diluted into the ambient atmosphere.

[0306] Compared with the prior art, this embodiment has the following beneficial effects:

[0307] (1) Achieved the structural optimization and energy efficiency improvement of the commercial air-conditioning main unit

[0308] The external heat exchanger assembly cavity 33 of this embodiment adopts a flat finned tube heat exchanger 1 to combine into a copper tube "IWI" type finned tube heat exchanger assembly structure. Among them, the copper tube M-shaped finned tube heat exchanger assembly part relies on the front air inlet surface for air supply; for the flat finned tube heat exchanger parts on both sides, in addition to a small amount of air supply from the front air inlet surface, the horizontal interval air supply on both sides of the air-conditioning main unit is mainly utilized.

[0309] The air path structure of the commercial air-conditioning main unit in this embodiment is optimized, and the entire area of the external facade of the equipment platform 36, the front of the commercial air-conditioning main unit, and the horizontal interval space adjacent to the main unit are used for air supply and exhaust;

[0310] In the copper tube "IWI" type finned tube heat exchanger assembly of the commercial air conditioner host in this embodiment, a refrigerant bypass pipeline 12 is provided to connect 6 flat finned tube heat exchangers 1 that make up the copper tube "IWI" shaped finned tube heat exchanger assembly; only one set of liquid distribution and collection lotus head 2 and gas collection and distribution pipe 3 are used to implement liquid distribution (collection) and gas collection (distribution) for the refrigerant branches 11 arranged on the 6 flat finned tube heat exchangers 1 of the copper tube "IWI" shaped finned tube heat exchanger assembly; moreover, the liquid distribution and collection lotus head 2 and the gas collection and distribution pipe 3 are arranged on different sides and are arranged on two side edges of two finned tube heat exchangers 1 of the copper tube "IWI" shaped finned tube heat exchanger assembly; thus, the fluorine circuit structure of the commercial air conditioner host in this embodiment is optimized, and the four-stage structure of the four finned tubes that make up the copper tube "IWI" shaped finned tube heat exchanger assembly effectively prevents the tendency that the wall surface temperatures of the refrigerant inlet and outlet of the entire copper tube "IWI" shaped finned tube heat exchanger assembly tend to be equalized due to the copper tube fin heat bridge, thereby causing the overall reduction of the heat transfer temperature difference between the refrigerant and the ambient air; at the same time, for the refrigerant branch 11 on the 4th flat finned tube heat exchanger 1 at the end of the condenser, when operating, the condensate inlet pipes of 2 adjacent refrigerant branches 11 are arranged "back to back", and the outlet pipes are also arranged "back to back", and the temperature gradient on the fin group between the inlet pipe with a higher temperature and the outlet pipe with the lowest temperature is the smallest, and the heat conduction intensity is the lowest, further deepening the "subcooling depth" of the condensate at the condenser outlet;

[0311] The comprehensive innovation of the above air circuit and fluorine circuit structures in this embodiment further improves the refrigeration capacity of the evaporator and the heat release of the condenser, and improves the energy efficiency ratio of the air conditioning system.

[0312] (2) Solved the problem of vertical transportation at the engineering site of the high-power commercial coupled air conditioner host

[0313] In this embodiment, the host structure of the commercial coupled air conditioner is decoupled and modularly designed. The host of the commercial air conditioner is decoupled into at least 3 first-level components such as a compressor cavity, an external heat exchanger assembly cavity, and a longitudinal exhaust cavity; its external heat exchanger assembly cavity and longitudinal exhaust cavity are in an upper and lower two-stage structure, and the compressor cavity is attached to the two-stage structure; the size of each first-level component is designed to meet the requirements of vertical transportation by ordinary elevators.

[0314] The 3 first-level components such as the compressor cavity, the longitudinal exhaust cavity, and the external heat exchanger assembly cavity in this embodiment are uniformly planned and balanced in technical parameters and structural dimensions, and are independently designed and manufactured. They can be transported to the equipment platform site by ordinary elevators and then assembled into the whole machine of the commercial coupled air conditioner.

[0315] (3) Provided necessary operating space for activities such as installation, maintenance, repair, and removal of the air conditioner host

[0316] The longitudinal exhaust air chamber, which is the lower segment of the two-section structure in this embodiment, extends outward on its three sides; the lateral extensions on both sides expand the width of the longitudinal exhaust air chamber, reduce the height of the longitudinal exhaust air chamber and the vertical ratio of the height of the longitudinal exhaust air chamber on the outer facade of the equipment platform, and set the lower limit of the lateral interval between the outer heat exchanger assembly cavities of adjacent air-conditioning main units; the longitudinal extension section on the front side is inserted forward above the counterfort of the equipment platform on the upper side of the chassis and is docked with the pre-set air outlet on the outer facade; the longitudinal extension section on the front side, together with the lateral extension sections on both sides, is connected to form a platform-style waistline of the main unit, providing the necessary operating space for operators to install, repair, maintain, and remove the outer heat exchanger assembly cavity of the air-conditioning main unit.

[0317] (4) Achieved the perfect combination of technological inheritance and innovation

[0318] This embodiment not only solves the two major scenario-based and technological practical technical problems of using an ordinary elevator for vertical transportation of the air-conditioning main unit and the operating space required for maintenance and repair activities of the air-conditioning main unit on the equipment platform 36, but also inherits the technology of an air-conditioning main unit with a vertically arranged fan 9 and its equipment platform 36 (application number 202310972409.9). It adopts excellent design technologies such as a corrugated fin tube heat exchanger assembly, the same-side upper and lower setting of the air inlet and air outlet, expanding the top space of the equipment platform 36, and constructing a decorative structure 40 with a low-resistance through the outer facade of the equipment platform 36 for the air path of the outer heat exchanger. It further explores the heat exchange potential of the redundant space at the top of the equipment platform 36, greatly improving the body load intensity of the air-conditioning main unit, the lateral line density of the load on the equipment platform 36, and the aesthetic degree of the outer facade of the equipment platform 36; in the scenario of a semi-enclosed building corridor (i.e., an embedded equipment platform 36), it innovatively designs the air-conditioning main unit body to achieve air path coupling and energy coupling between the air-conditioning main unit and the decorative structure 40 of the building outer facade, achieving the perfect combination of technological inheritance and innovation.

[0319] Obviously, the above-mentioned embodiments of the present invention are merely examples for clearly illustrating the present invention, rather than limitations on the implementation manners of the present invention. For those of ordinary skill in the art, other different forms of changes or modifications can be made based on the above description. It is not necessary and impossible to enumerate all the implementation manners here. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present invention shall be included in the protection scope of the claims of the present invention.

Claims

1. A finned tube heat exchanger assembly, characterized in that, It includes a finned-tube heat exchanger, 1 liquid-distributing and collecting lotus head, and 1 gas-collecting and distributing pipe; The finned-tube heat exchanger includes, but is not limited to, single-row tube, double-row tube, triple-row tube, quadruple-row tube, and quintuple-row tube finned-tube heat exchangers; the finned-tube heat exchanger includes several refrigerant branches; the liquid-phase interfaces of the fluorine circuits of each refrigerant branch are connected to the liquid-distributing and collecting lotus head, and the gas-phase interfaces of the fluorine circuits are connected to the gas-collecting and distributing pipe; The liquid-distributing and collecting lotus head and the gas-collecting and distributing pipe are arranged at the same side end plate of the finned-tube heat exchanger; The refrigerant liquid pipes of 2 refrigerant branches connected to the liquid-distributing and collecting lotus head are arranged adjacent to each other on the same set of fin plates of the same row of finned-tube heat exchanger.

2. The finned tube heat exchanger assembly according to claim 1, wherein, 2 adjacent refrigerant branches form a refrigerant pipeline module unit, and the 2 refrigerant liquid pipes in the refrigerant pipeline module unit are arranged adjacent to each other on the same set of fin plates of the same row of finned-tube heat exchanger; Alternatively, the 2 refrigerant liquid pipes of 2 adjacent refrigerant pipeline module units are arranged adjacent to each other on the same set of fin plates of the same row of finned-tube heat exchanger.

3. The finned tube heat exchanger assembly according to claim 2, characterized in that, The refrigerant gas pipes connected to the gas-phase interfaces of 2 adjacent refrigerant pipeline module units are arranged adjacent to each other on the same set of fin plates of the same row of finned-tube heat exchanger; or, the 2 refrigerant gas pipes of the refrigerant pipeline module unit are arranged adjacent to each other on the same set of fin plates of the same row of finned-tube heat exchanger.

4. A finned tube heat exchanger assembly, characterized in that, It includes several flat-plate finned-tube heat exchangers, 1 liquid-distributing and collecting lotus head, and 1 gas-collecting and distributing pipe; The flat-plate finned-tube heat exchanger includes, but is not limited to, single-row tube, double-row tube, triple-row tube, quadruple-row tube, and quintuple-row tube finned-tube heat exchangers; The flat-plate finned-tube heat exchanger includes several refrigerant branches; The refrigerant branches between different flat-plate finned-tube heat exchangers are connected in series through refrigerant crossover pipelines; The refrigerant branches are connected to the liquid-distributing and collecting lotus head and the gas-collecting and distributing pipe to form a finned-tube heat exchanger assembly.

5. The finned tube heat exchanger assembly according to claim 4, characterized in that, The liquid-distributing and collecting lotus head and the gas-collecting and distributing pipe are arranged at the same side end plate of the same flat-plate finned-tube heat exchanger; or are respectively arranged at the end plates of different flat-plate finned-tube heat exchangers.

6. The finned tube heat exchanger assembly according to claim 4, wherein, Adjacent flat-plate finned-tube heat exchangers are connected through refrigerant crossover pipelines to connect the refrigerant branches, and the superheat heat exchange section, phase change heat exchange section, and subcooling heat exchange section of any refrigerant branch between the gas-collecting and distributing pipe and the liquid-distributing and collecting lotus head are distributed in each flat-plate finned-tube heat exchanger; or, any refrigerant branch between the gas-collecting and distributing pipe and the liquid-distributing and collecting lotus head is segmented and arranged in each flat-plate finned-tube heat exchanger.

7. The finned tube heat exchanger assembly according to claim 4, wherein The refrigerant liquid pipes of 2 refrigerant branches connected to the liquid-distributing and collecting lotus head are arranged adjacent to each other on the same set of fin plates of the same row of finned-tube heat exchanger.

8. The finned tube heat exchanger assembly according to claim 4, wherein The refrigerant gas pipes of 2 refrigerant branches connected to the gas-collecting and distributing pipe are arranged far from each other on the same set of fin plates of the same row of finned-tube heat exchanger.

9. The finned tube heat exchanger assembly according to claim 4, wherein, The total length of the refrigerant pipelines of any refrigerant branch between the gas-collecting and distributing pipe and the liquid-distributing and collecting lotus head is equal or substantially equal.

10. An air conditioner main unit, characterized in that, It includes the finned-tube heat exchanger assembly according to any one of claims 1-9.

11. The air conditioner main unit according to claim 10, characterized in that, The air-conditioning main unit includes a housing, a negative pressure chamber, an exhaust chamber, a compressor chamber, and a fan; The negative pressure chamber and the exhaust chamber are arranged side by side; the compressor chamber is arranged outside the first back plate of the negative pressure chamber and / or the exhaust chamber; The air inlet direction of the fan is orthogonally arranged or nearly orthogonally arranged with the main air outlet direction of the finned tube heat exchanger assembly, so as to construct an air flow vortex chamber between the air outlet of the finned tube heat exchanger assembly in the negative pressure chamber and the air inlet of the fan.

12. The air conditioner main unit according to claim 10, characterized in that, The air conditioner main unit includes a housing, a negative pressure chamber, an exhaust chamber, a compressor chamber and a fan; The compressor chamber and the exhaust chamber are arranged side by side outside the same side plate of the negative pressure chamber; The air inlet direction of the fan is orthogonally arranged or nearly orthogonally arranged with the main air outlet direction of the finned tube heat exchanger assembly, so as to construct an air flow vortex chamber between the air outlet of the finned tube heat exchanger assembly in the negative pressure chamber and the air inlet of the fan.

13. The air conditioner main unit according to claim 10, wherein It is composed of module assembly. The module includes a compressor cavity provided with a compressor, an external heat exchanger assembly cavity provided with a finned tube heat exchanger assembly and a vertical exhaust chamber, and a longitudinal exhaust chamber communicated with the vertical exhaust chamber; The longitudinal exhaust chamber is arranged below or above the external heat exchanger assembly cavity and is fixedly connected to the bottom plate or the top plate of the vertical exhaust chamber; The compressor cavity is arranged on the side of the longitudinal exhaust chamber and is communicated with the external heat exchanger assembly cavity for fluorine circuit and electric circuit; The air outlet of the longitudinal exhaust chamber has the same orientation as the air inlet of the finned tube heat exchanger assembly.

14. The air conditioner main unit according to claim 13, characterized in that, The horizontal cross-sectional dimension of the longitudinal exhaust chamber is greater than or equal to the horizontal cross-sectional dimension of the external heat exchanger assembly cavity; The back plate of the external heat exchanger assembly cavity is flush with the back plate of the longitudinal exhaust chamber; the compressor cavity is arranged on the back plate of the longitudinal exhaust chamber.

15. A device platform, characterized in that, The equipment platform is provided with the air conditioner main unit according to any one of claims 10-14.

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