Liquid homogenizing assembly and heat exchanger

Abstract

The utility model provides a liquid homogenizing assembly and a heat exchanger. The liquid uniformizing assembly comprises a body, a liquid uniformizing partition plate and a plurality of branch pipes. The body is in a hollow column shape and is provided with a liquid inlet hole, a plurality of liquid outlet holes and a containing cavity. The liquid uniformizing partition plate is arranged in the containing cavity in the axial direction perpendicular to the body, a distribution cavity communicated with the liquid outlet holes is defined between the liquid uniformizing partition plate and the liquid outlet end of the body, and multiple circles of partition plate holes distributed around the axis of the body in an annular array mode are formed in the liquid uniformizing partition plate in the radial direction; and the plurality of circles of partition plate holes are positioned on the peripheral plane of the projection area of the liquid inlet holes on the liquid homogenizing partition plate. Wherein the liquid outlet holes form a plurality of circles of annular columns in the circumferential direction of the body, the liquid outlet holes in each circle are distributed in one-to-one correspondence with the partition plate holes in the corresponding circle through the distribution cavity, and the branch pipes are welded in the corresponding liquid outlet holes respectively.

Description

Technical Field

[0001] This utility model relates to the field of refrigeration accessories, and in particular to a liquid equalization component and a heat exchanger. Background Technology

[0002] To improve heat exchange efficiency, existing refrigeration system heat exchangers typically employ a multi-flow-path design. During operation, the two-phase refrigerant, after being throttled by the expansion valve, needs to be evenly distributed to each branch of the heat exchanger. A shell-and-tube heat exchanger is a type of indirect heat exchange device that uses the wall surface of a tube bundle enclosed within a shell as the heat transfer surface. Its heat exchange medium is generally water and refrigerant. Compared to other heat exchangers (such as coaxial heat exchangers, plate heat exchangers, and high-efficiency tank heat exchangers), shell-and-tube heat exchangers not only have advantages in terms of low water resistance and refrigerant flow resistance, but also a significant price advantage. Shell-and-tube heat exchangers are divided into dry heat exchangers and flooded heat exchangers. In a dry heat exchanger, the tube-side medium is a mixture of gas and liquid refrigerant. When the two-phase refrigerant enters the tube box, the combined effects of gravity and expansion cause gas-liquid separation, making it difficult to evenly distribute the liquid refrigerant to each heat exchange tube. Especially when the two-phase refrigerant impacts the tube sheet at high speed, it can trigger severe turbulence, vortices, and foaming, exacerbating the uneven distribution problem. This uneven distribution in the perforated plate structure not only reduces heat exchange efficiency but may also cause damage to the compressor if some liquid refrigerant in the heat exchange tubes fails to evaporate completely, resulting in the evaporated gaseous refrigerant carrying droplets into the compressor.

[0003] To improve the uniformity of refrigerant distribution, shell-and-tube heat exchangers with distributors have been proposed. In this structure, the distributor is a one-piece conical distributor made of copper. The conical distributor accelerates the two-phase flow through its throat, promoting mixing and then uniformly distributing the refrigerant into annular inclined channels that are all connected to the throat and arranged in a ring around the distribution cone. However, limited by the conical structure and the spatial layout of the annular inclined channels, the branch pipes on this type of distributor can only be distributed in a single-ring array at the liquid outlet end. Increasing the number of branch pipes leads to a significant increase in the overall geometric dimensions; this not only significantly increases the material cost of the distributor but also creates compatibility barriers due to the size limitations of existing shell-and-tube heat exchanger tube sheets, making it difficult to apply. In addition, tubular distributors (such as...) have also been proposed. Figure 1 As shown in the diagram, this scheme achieves refrigerant distribution by opening liquid inlet pipes 601 and multiple distribution pipes 602 on both sides of the long tube body 600. However, in this scheme, the flow channel lengths from each distribution hole to the liquid inlet hole are different. The refrigerant will preferentially enter the corresponding heat exchange tube through the distribution hole with the shorter flow channel, causing an imbalance in the two-phase refrigerant distribution. The superposition of gravity and refrigerant expansion will further exacerbate the uneven distribution problem. Furthermore, Chinese patent CN117387254A also proposes an evaporator structure with baffles and gaseous refrigerant distribution pipes inside the tube box, which adopts a gas-liquid separation design for refrigerant distribution. However, its core gaseous refrigerant distribution pipe still uses... Figure 1This type of tubular distributor, inherently flawed in its unequal flow channel spacing, results in uneven distribution of gaseous refrigerant, preventing it from uniformly tearing the liquid refrigerant. Simultaneously, the separated liquid refrigerant, due to its decreased flow velocity, deposits at the bottom of the liquid refrigerant distribution chamber under gravity, causing an imbalance in the secondary distribution of the liquid refrigerant. Furthermore, the gas-liquid separation and re-impact mixing design of this scheme will lead to increased complexity and soaring manufacturing costs. Utility Model Content

[0004] In order to overcome the shortcomings of the prior art, this utility model provides a liquid equalization component and a heat exchanger.

[0005] To achieve the above objectives, this utility model provides a liquid equalization assembly, which includes a body, a liquid equalization baffle, and multiple branch pipes. The body is a hollow column with an inlet hole, multiple outlet holes, and a receiving cavity. The liquid equalization baffle is disposed in the receiving cavity along an axial direction perpendicular to the body. A distribution cavity connecting the multiple outlet holes is formed between the liquid equalization baffle and the outlet end of the body. The liquid equalization baffle has multiple rings of baffle holes arranged radially in a circular array around the axis of the body, and the multiple rings of baffle holes are located on the outer peripheral plane of the projection area of ​​the inlet hole on the liquid equalization baffle.

[0006] Multiple liquid outlet holes form multiple rings along the circumference of the body. Each ring of liquid outlet holes is distributed one-to-one with the partition holes on the corresponding ring through the distribution cavity. Multiple branch pipes are welded into the corresponding liquid outlet holes.

[0007] According to one embodiment of the present invention, multiple partition holes on each ring are evenly spaced at equal center distances, and the center distance between two adjacent partition holes on the i-th ring is L. i The center distance between two adjacent diaphragm holes on the j-th ring is L. j The difference in center distance between any two rings of diaphragm holes is ΔL ij =∣L i -L j |≤1.2mm.

[0008] According to one embodiment of the present invention, at least a portion of the branch pipe has a bend near the liquid outlet end of the main body. When the bend angle at the bend is greater than or equal to 10 degrees, the length L of the straight pipe section between the upstream end of the bend and the end of the branch pipe inserted into the liquid outlet hole is ≥8mm.

[0009] According to one embodiment of the present invention, the liquid equalization assembly further includes a straight pipe sleeve that is fitted over the straight pipe section and inserted into the liquid outlet hole. The curved portion on the branch pipe is located at the downstream end of the straight pipe sleeve. The length of the straight pipe section is determined based on the straight pipe sleeve when the curved portion is formed.

[0010] According to one embodiment of the present invention, the partition hole is a through hole or a flanged hole extending into the distribution cavity, and the diameter of the partition hole is basically the same or gradually decreases along its extension direction.

[0011] Alternatively, the baffle hole is an arc bubble hole whose wall protrudes arc-shaped towards one or both sides of the liquid equalization baffle.

[0012] According to one embodiment of the present invention, the liquid equalization baffle is a plate structure with both sides being nearly planar;

[0013] Alternatively, the projection area of ​​the liquid inlet on the liquid equalization baffle protrudes to one side of the liquid equalization baffle, and the longitudinal cross-sectional outline of the protrusion is one or more combinations of square, trapezoidal, triangular or partially circular.

[0014] According to one embodiment of the present invention, the liquid equalization assembly further includes a flow guide disposed in the distribution cavity and located on the inner periphery of the multiple liquid outlet holes, and the flow guide and the peripheral wall of the body form an annular flow channel connecting the multiple liquid outlet holes.

[0015] According to one embodiment of the present invention, the flow guide is a cylindrical septum, one end of which abuts against the liquid equalization septum area on the inner circumference of the multi-ring septum hole, and the other end abuts against the liquid outlet end of the body on the inner circumference of the multi-ring liquid outlet hole; or, the flow guide is a flow guide cone, the bottom of which is located at the liquid outlet end of the body on the inner circumference of the multi-ring liquid outlet hole, and its end extends toward the liquid equalization septum.

[0016] According to one embodiment of the present invention, the projection area of ​​the liquid inlet hole on the liquid equalization baffle protrudes into the distribution cavity and abuts against the inner wall of the liquid outlet end of the body to form a mixing cavity; the radial distance L1 from the outer peripheral wall of the mixing cavity to the inner edge of the innermost liquid outlet hole satisfies: L1≤4mm;

[0017] Alternatively, the radial distance L1 from the outer peripheral wall of the diaphragm to the inner edge of the innermost liquid outlet hole satisfies: L1≤4mm;

[0018] The inner edge of the innermost liquid outlet refers to the intersection of the line connecting the center of the innermost liquid outlet and the center of the liquid outlet of the main body with the edge of the innermost liquid outlet on the liquid outlet end of the main body.

[0019] According to one embodiment of the present invention, the liquid equalization assembly further includes a jetting element disposed in the distribution cavity, the jetting element having a jetting hole formed thereon and the jetting hole being opposite to the projection area of ​​the liquid inlet hole on the liquid equalization partition.

[0020] According to one embodiment of the present invention, the liquid equalization assembly further includes a reflective mixing guide plate disposed in the distribution cavity and located downstream of the jet member. The reflective mixing guide plate has multiple rings of guide holes that correspond one-to-one with multiple liquid outlet holes and are distributed in a ring array. The multiple rings of guide holes are distributed on the outer peripheral plane of the projection area of ​​the jet hole on the reflective mixing guide plate.

[0021] Alternatively, the liquid equalization assembly may also include a flow guide placed in the distribution chamber and downstream of the jet component. The flow guide is located on the inner circumference of the multiple liquid outlet holes, and an annular flow channel connecting the multiple liquid outlet holes is formed between the flow guide and the peripheral wall of the body.

[0022] According to one embodiment of the present invention, when the projection area of ​​the liquid inlet hole on the liquid equalization baffle protrudes towards the side where the jet component is located, the liquid equalization assembly further includes a partition plate disposed between the liquid equalization baffle and the jet component. The partition plate divides the flow pattern maintenance cavity enclosed by the liquid equalization baffle and the jet component into a first maintenance cavity and a second maintenance cavity. A plurality of partition plate through holes are formed on the partition plate to connect the first maintenance cavity and the second maintenance cavity. The pre-rectification cavity volume V1, the first maintenance cavity volume V21, and the second maintenance cavity volume V22 enclosed between the liquid equalization baffle and the liquid inlet end of the main body satisfy the following: 0.75≤V1 / V21≤1.3, 0.75≤V21 / V22≤1.3.

[0023] According to one embodiment of the present invention, the liquid equalization assembly further includes a liquid inlet pipe welded to the liquid inlet hole. The liquid inlet pipe has a main body section with a basically unchanged inner diameter and a jet section located downstream of the main body section with a smaller inner diameter than the main body section. The jet section is a straight section with a smaller inner diameter than the main body section or a Venturi tube section with a jet throat.

[0024] According to one embodiment of the present invention, the branch pipe is an integral pipe fitting with a basically uniform inner diameter; or, the branch pipe includes a connecting section and a branch pipe extension section, and the inner diameter of the connecting section is greater than or equal to the inner diameter of the branch pipe extension section.

[0025] On the other hand, this utility model also provides a heat exchanger that includes the above-mentioned liquid equalization component.

[0026] According to one embodiment of the present invention, the heat exchanger is a shell-and-tube heat exchanger, and the multiple branch pipes on the liquid equalization assembly are respectively assembled one-to-one with the multiple heat exchange tubes on the shell-and-tube heat exchanger.

[0027] In summary, the liquid equalization assembly provided by this utility model divides the internal cavity of the main body into two or more chambers through a liquid equalization baffle, providing space for refrigerant mixing and distribution while suppressing the problem of excessive refrigerant expansion caused by an excessively large cavity. The main body adopts a hollow cylindrical design, and its internal cavity cross-section and the multiple rings of baffle holes on the liquid equalization baffle are based on a circular topology optimization structure, which significantly improves the uniformity of distribution through geometric symmetry. This cylindrical structure forms a cylindrical distribution cavity with the liquid equalization baffle and the liquid outlet end of the main body. The multiple rings of liquid outlet holes can be distributed based on the one-to-one correspondence between the cylindrical distribution cavity and the multiple rings of baffle holes. Under the condition of keeping the radial dimension of the main body unchanged, the number of branch pipes can be increased many times compared with the traditional single-ring distribution scheme. By arranging multiple rings of baffle holes on the outer periphery of the liquid inlet projection area, the dynamic blocking and reflection of the input refrigerant by the projection area is used to enhance the mixing degree of the two-phase refrigerant. Combined with the staggered arrangement strategy of the multiple rings of baffle holes and the liquid inlet, the flow resistance of each baffle hole is balanced while preventing the refrigerant from flowing directly through, thus creating conditions for the refrigerant to be fully mixed before entering the multiple rings of baffle holes.

[0028] To make the above and other objects, features and advantages of this utility model more apparent and understandable, preferred embodiments are described below in detail with reference to the accompanying drawings. Attached Figure Description

[0029] Figure 1 The diagram shown is a structural schematic of an existing tubular distributor.

[0030] Figure 2 The diagram shown is a schematic diagram of the liquid homogenization component provided in Embodiment 1 of this utility model.

[0031] Figure 2A As shown Figure 2 Assembly diagram of the main body and the inlet pipe.

[0032] Figure 3 As shown Figure 2 Enlarged diagram of point A in the middle.

[0033] Figure 4 As shown Figure 2 A schematic diagram of the structure after removing part of the branch pipe.

[0034] Figure 5 As shown Figure 2 A schematic diagram of the structure of the equalization liquid partition.

[0035] Figure 6 As shown Figure 5 A projection diagram.

[0036] Figure 7 and Figure 8 The diagram shown is a partial schematic of a liquid homogenization component provided in another embodiment of the present invention.

[0037] Figure 9 The diagram shown is a partial schematic of the liquid equalization component provided in Embodiment 2 of this utility model.

[0038] Figure 10 The diagram shown is a partial schematic of a shell-and-tube heat exchanger provided in another embodiment of this utility model.

[0039] Figure 11 The diagram shown is a schematic diagram of the liquid equalization component provided in Embodiment 3 of this utility model.

[0040] Figure 12 As shown Figure 11 A schematic diagram of the structure of the equalization liquid partition.

[0041] Figure 13 for Figure 12 A cross-sectional view.

[0042] Figure 14 , Figure 15 as well as Figure 16A schematic diagram of the liquid equalization partition in a liquid equalization assembly provided in another embodiment of the present invention.

[0043] Figure 17 The diagram shown is a partial schematic of a liquid homogenization component provided in another embodiment of the present invention.

[0044] Figure 18 The diagram shown is a partial schematic of the liquid equalization component provided in Embodiment 4 of this utility model.

[0045] Figure 19 , Figure 20 , Figure 20 , Figure 21 as well as Figure 22 The diagram shown is a partial schematic of a liquid homogenization component provided in another embodiment of the present invention.

[0046] Figure 23 The diagram shown is a partial schematic of the liquid equalization component provided in Embodiment 5 of this utility model.

[0047] Figure 24 As shown Figure 23 A schematic diagram of the middle partition plate.

[0048] Figure 25 The diagram shown is a partial schematic of a liquid homogenization component provided in another embodiment of the present invention. Detailed Implementation

[0049] In this application, the distinction between upstream and downstream is based on the direction of refrigerant flow. Generally, refrigerant flows from upstream to downstream, and the downstream area receives refrigerant from upstream. When the distributor is installed vertically or at an angle, with the inlet of the distributor located below the outlet along the direction of gravity, the inertial force of the refrigerant inside the distributor overcomes gravity and flows in the opposite direction of gravity; in this case, upstream and downstream are still distinguished according to the direction of refrigerant flow.

[0050] Example 1

[0051] In existing shell-and-tube heat exchangers, the two-phase refrigerant enters the tube box and is directly distributed to multiple heat exchange tubes connected to the tube sheet. This refrigerant distribution method using an orifice plate structure not only has low heat exchange efficiency but also poses a risk of liquid carryover during compressor suction due to incomplete evaporation of the liquid refrigerant in some heat exchange tubes. To solve this problem, some have proposed introducing a liquid distribution assembly into the shell-and-tube heat exchanger. However, this technology faces several bottlenecks: conical liquid distribution assemblies are limited by space constraints, making branch pipe expansion difficult and thus unsuitable for multi-tube heat exchangers; tubular liquid distribution assemblies (such as...) Figure 1 As shown, the uneven spacing of the flow channels leads to distribution imbalance; the gas-liquid separation type liquid equalization component not only inherits the defects of the tubular type liquid equalization component but also has a complex structure.

[0052] In view of this, the present invention provides a liquid distribution assembly with excellent distribution performance and a branch pipe number that can be adapted to heat exchange tubes of different specifications. For example... Figures 2 to 6 As shown, the liquid equalization assembly provided in this embodiment includes a body 1, a liquid equalization baffle 2, and multiple branch pipes 3. The body 1 is a hollow column with an inlet hole 11, multiple outlet holes 12, and a receiving cavity 13. The liquid equalization baffle 2 is arranged in the receiving cavity 13 along an axial direction perpendicular to the body 1. A distribution cavity 130 is formed between the liquid equalization baffle 2 and the outlet end of the body 1, connecting the multiple outlet holes 12. The liquid equalization baffle 2 has multiple rings of baffle holes 21 arranged radially around the axis of the body 1 in a circular array, and the multiple rings of baffle holes 21 are located on the outer peripheral plane of the projection area 22 of the inlet hole 11 on the liquid equalization baffle 2. The multiple outlet holes 12 form multiple rings along the circumference of the body 1. Each ring of outlet holes 12 is distributed one-to-one with the baffle holes 21 on the corresponding ring through the distribution cavity 130. The multiple branch pipes 3 are respectively welded to the corresponding outlet holes 12.

[0053] For the multi-ring liquid outlet holes 12: Preferably, each liquid outlet hole 12 is coaxially aligned with the corresponding partition hole 21 via a cylindrical distribution cavity 130. However, this invention does not impose any limitation on this. In other embodiments, there may be a certain distance between the axis of the liquid outlet hole and the axis of the partition hole. More preferably, in this embodiment, the diameter of each partition hole 21 is substantially close to the diameter of the corresponding liquid outlet hole 12. However, this invention does not impose any limitation on this. In other embodiments, the diameter of the partition hole may also be larger or smaller than the diameter of the corresponding liquid outlet hole.

[0054] The liquid equalization assembly provided in this embodiment uses a liquid equalization baffle 2 to divide the accommodating cavity 13 within the main body 1 into a dual-function chamber for mixing and distribution. This provides space for refrigerant mixing and effectively suppresses excessive refrigerant expansion by limiting the cavity volume. Based on this, the baffle holes 21 are designed in a multi-ring array according to the circular inner cavity cross-section of the cylindrical main body 1. These multiple rings of baffle holes 21 then form a one-to-one spatial mapping relationship with the multiple rings of liquid outlet holes 12 on the liquid outlet end of the main body 1 through the cylindrical distribution cavity 130. This layout allows the liquid equalization assembly provided in this embodiment to achieve a significant increase in the number of branch pipes 3 while maintaining the same radial dimension of the main body 1, effectively solving the problem that existing liquid equalization assemblies are difficult to adapt to multiple heat exchange tubes on shell-and-tube heat exchangers due to the limited number of branch pipes 3. Furthermore, on the liquid equalization baffle 2, by arranging the baffle holes 21 on the outer peripheral plane of the projection area 22, the projection area 22 is used to block and reflect the input refrigerant, thereby enhancing the mixing of the gas and liquid two-phase refrigerant and reshaping the refrigerant flow pattern to develop into a fully mixed, diffuse flow pattern, thus improving the distribution uniformity. At the same time, the staggered arrangement of the multiple rings of baffle holes 21 and the liquid inlet holes 11 not only balances the flow path of each baffle hole 21, but also effectively prevents the refrigerant from flowing directly into the distribution chamber 130 before it has time to mix, providing conditions for the two-phase refrigerant to be fully mixed and then redistributed.

[0055] In this embodiment, as Figure 2 As shown, the main body 1 includes a cylindrical tube 1A, an end cap 1B, and a liner 1C, which together form a receiving cavity 13. The end cap 1B is sealed and welded to the liquid inlet end of the cylindrical tube 1A and has a liquid inlet hole 11 formed thereon. The liner 1C is embedded in and sealed and welded to the liquid outlet end of the cylindrical tube 1A, and multiple rings of liquid outlet holes 12 are formed on the liner 1C by stamping. However, this utility model does not limit this in any way. In other embodiments, the main body 1' may also include a cylindrical tube 1A' with one open end and an end cap 1B. The end cap 1B is sealed and welded to the open end of the cylindrical tube 1A' and has a liquid inlet hole 11 formed thereon. The bottom of the cylindrical tube 1A' is stamped to form multiple rings of cylindrical through holes to form multiple rings of liquid outlet holes 12. Specifically, in Figure 7 In this embodiment, the main body 1 also includes a liner 1C disposed on the inner bottom wall of the cylindrical body 1A'. The liner 1C has liner through holes distributed one-to-one with the multiple cylindrical through holes. The liner through holes and the corresponding cylindrical through holes together form a liquid outlet hole 12. Alternatively, in other embodiments, the main body includes an end cap and a liner. The end cap has a liquid inlet hole, and the open end of the end cap has a cylindrical straight section. The liner is embedded in and sealed and welded to the cylindrical straight section to form a receiving cavity. The liner has multiple liquid outlet holes formed by stamping.

[0056] In this embodiment, as Figure 5 and Figure 6 As shown, the liquid equalization baffle 2 employs a concentric multi-ring array for the design of the baffle holes 21 to achieve precise distribution. For multiple baffle holes 21 distributed within the same ring, an equal center-distance layout is used to ensure that the flow paths of each baffle hole 21 are basically consistent, thereby achieving uniform distribution within that ring. Regarding cross-ring arrangements, the center-distance between adjacent baffle holes 21 in the i-th ring is defined as L. i The center distance between adjacent diaphragm holes 21 on the j-th ring is L. j By constraining the difference in center distance between any two rings of diaphragm holes

[0057] △L 12 =|L1-L2|≤1.2mm, ensuring similar refrigerant flow characteristics between different rings, thereby achieving control over the uniformity of flow distribution in the multi-ring baffle holes 21. In this embodiment, two rings of baffle holes 21 are formed on the liquid equalization baffle 2. The center distance between two adjacent baffle holes 21 on the inner ring is L1, and the center distance between two adjacent baffle holes 21 on the outer ring is L2. The difference in center distance between the inner and outer ring baffle holes is ΔL. 12 = |L1-L2| ≤ 1.2mm. Preferably, the center distance difference ΔL between any two rings of partition holes can be set. ij The value is 0.2mm, 0.5mm, 0.8mm, 1mm or other values ​​less than or equal to 1.2mm.

[0058] Although this embodiment uses a liquid equalization baffle 2 with two rings of baffle holes 21 as an example, the present invention does not limit this. In other embodiments, the liquid equalization baffle may also have multiple rings of baffle holes, such as three or more rings. Taking three rings of baffle holes as an example, the center distance difference between the first and second rings of baffle holes is ΔL. 12 The center distance difference between the holes in the first and third rings is ΔL. 13 The center distance difference between the holes in the second and third rings is ΔL. 23 ; △L 12 , △L 13 and △L 23 All are less than or equal to 1.2 mm, and this utility model does not impose any limitation on whether the differences in the center distances of the three are equal.

[0059] In this embodiment, as Figure 5 and Figure 6 As shown, the liquid equalization baffle 2 is a plate structure with both sides being nearly planar. The projection area 22 of the liquid inlet hole 11 on the liquid equalization baffle 2 is also planar. The multiple rings of baffle holes 21 are located on the plane of the liquid equalization baffle 2 around the projection area 22. However, this utility model does not impose any limitations on this.

[0060] In this embodiment, the baffle hole 21 is a flanged hole with an arc-shaped inner wall generatrix and a gradually decreasing diameter along the refrigerant flow direction. The gradual reduction in the inner diameter of the baffle hole 21 can accelerate the flowing refrigerant, increasing the refrigerant flow rate so that it can quickly enter the corresponding liquid outlet hole 12; in addition, the acceleration of the baffle hole 21 can further promote the mixing of the gas and liquid two-phase refrigerant. However, this utility model does not limit this in any way. In other embodiments, the baffle hole can be an arc-shaped bubble hole with the hole wall protruding arc-shaped towards one or both sides of the liquid equalization baffle. Alternatively, the baffle hole can be a collecting hole with an inclined straight inner wall generatrix and a gradually decreasing diameter along the refrigerant flow direction. Alternatively, the baffle hole can be a through hole with a diameter that is basically the same along the refrigerant flow direction (e.g., Figure 7 and Figure 8 (as shown) and the shape of the through hole is any one or a combination of circular, elliptical or oblong.

[0061] For a branch pipe 3 arranged in a ring array, when it is assembled with multiple heat exchange tubes arranged in rows and columns within a shell-and-tube heat exchanger, at least a portion of the branch pipe 3 inevitably forms a bend 31 near the liquid outlet end of the main body 1. This bend 31 alters the end position to accommodate the corresponding heat exchange tube ports, thereby connecting the liquid distribution assembly and the multiple heat exchange tubes. However, the bend in the branch pipe 3 changes the direction of its internal flow channel. When the refrigerant output from the liquid outlet 12 reaches the bend 31, it is blocked by the inner wall of the outer side of the bend 31 (the inner wall furthest radially from the center of the bend), and some of the refrigerant is reflected upstream. The pressure wave generated by this reflection continues to propagate upstream. This pressure wave, acting in the opposite direction to the refrigerant flow, hinders the refrigerant from entering the liquid outlet 12, affecting the refrigerant distribution within the branch pipe 3 and causing uneven distribution problems. Furthermore, the influence of the reflected pressure wave increases with the increase of the bending angle θ, where the bending angle θ refers to the angle between the extended line of the central axis at the upstream end of the bend 31 and the extended line of the central axis at the downstream end of the bend 31, such as... Figure 4 As shown.

[0062] To reduce the impact of the bend 31 on the uniformity of refrigerant distribution, this embodiment sets the length L of the straight pipe section 32 from the upstream end of the bend 31 to the inner end of the branch pipe 3 inserted into the outlet hole 12 to be greater than or equal to 10 degrees. Figure 4 As shown. This embodiment provides an attenuation distance for the reflected pressure wave by setting the length L of the straight pipe section 32, ensuring that the pressure wave is completely attenuated before reaching the liquid outlet 12, thereby effectively solving the problem of the downstream pressure wave reflection caused by the bend 31 affecting the uniformity of refrigerant distribution at the liquid outlet 12. Preferably, the length L of the straight pipe section 32 can be set to a value of 10 mm, 15 mm, 18 mm, or 20 mm or more.

[0063] When the branch pipe 3 is bent, in order to accurately control the required length L of the straight pipe section 32, this embodiment of the liquid equalization assembly also includes a straight pipe sleeve 4 that is fitted over the straight pipe section 32 and inserted into the liquid outlet 12. The bent portion 31 on the branch pipe 3 is located at the downstream end of the straight pipe sleeve 4. When forming the bent portion 31, the length of the straight pipe section 32 is accurately controlled based on the straight pipe sleeve 4, such as... Figure 3 and Figure 4 As shown. In addition, the straight pipe sleeve 4 can also protect the root of the branch pipe 3 (i.e., the connection between the branch pipe 3 and the body 1) during bending, so as to avoid the root of the branch pipe 3 from breaking due to excessive bending angle, and improve the reliability of bending process.

[0064] In this embodiment, branch pipe 3 is an integral pipe fitting with a substantially uniform inner diameter. However, this utility model does not impose any limitations on this. In other embodiments, the branch pipe may also include a connecting section and a branch pipe extension section, and the inner diameter of the connecting section is greater than or equal to the inner diameter of the branch pipe extension section.

[0065] In this embodiment, as Figure 2 As shown, the liquid equalization assembly also includes a liquid inlet pipe 5 welded to the liquid inlet hole 11. The liquid inlet pipe 5 has a main body section 51 with a basically unchanged inner diameter and a jet section 52 located downstream of the main body section 51 with a smaller inner diameter than the main body section 51. The jet section 52 accelerates the refrigerant to promote the mixing of the gas-liquid two-phase refrigerant while increasing the kinetic energy of the refrigerant. The high-speed refrigerant jet is injected into the projection area 22 of the liquid inlet hole 11 on the liquid equalization baffle 2 to enhance the reflection effect. Figure 2 In this embodiment, the jet section 52 is a straight section with a reduced inner diameter relative to the main body section 51. However, this invention does not limit this to any particular type; in other embodiments, the jet section 52 may also be a venturi tube section with a jet throat, such as... Figure 7 As shown.

[0066] Correspondingly, this embodiment also provides a heat exchanger including the above-mentioned liquid equalization component. This heat exchanger is a shell-and-tube heat exchanger, and the multiple branch pipes 3 on the liquid equalization component are respectively assembled one-to-one with the multiple heat exchange tubes on the shell-and-tube heat exchanger. Specifically, each branch pipe 3 is directly and sealed to the corresponding heat exchanger port; or, each branch pipe can also be sealed to the corresponding heat exchanger port through the tube sheet assembly on the shell-and-tube heat exchanger.

[0067] Although this embodiment uses the application of the liquid equalization component in a shell-and-tube heat exchanger as an example, the present invention does not limit it in any way. In other embodiments, the liquid equalization component provided by the present invention can also be applied to other heat exchangers with many branches, such as shell-and-tube heat exchangers, plate heat exchangers, high-efficiency tank heat exchangers, and microchannel heat exchangers.

[0068] Example 2

[0069] This embodiment is basically the same as Embodiment 1 and its variations, except that: Figure 9 As shown, the liquid equalization assembly also includes a flow guide 6 disposed in the distribution cavity 130 and located on the inner periphery of the multi-ring liquid outlet holes 12. The flow guide 6 and the peripheral wall of the body 1 form an annular flow channel that connects the multi-ring liquid outlet holes 12.

[0070] In this embodiment, the volume of the distribution cavity 130 is reduced by setting the flow guide 6 to maintain the refrigerant flow rate ejected from the multi-ring baffle holes 21, ensuring that the refrigerant has sufficient inertial force within the distribution cavity 130 to overcome the influence of gravity and avoid gas-liquid two-phase segregation of the mixed refrigerant. At the same time, the annular flow channel formed by the flow guide 6 and the inner wall of the distribution cavity 130 can also uniformly guide the fully mixed homogeneous refrigerant into the multi-ring liquid outlet holes 12.

[0071] In the shell-and-tube heat exchanger provided in this embodiment, although a flow guide 6 is provided inside the liquid distribution assembly, the flow guide 6 is located on the inner circumference of the multi-ring liquid outlet holes 12, and it will not affect the processing arrangement of the multi-ring liquid outlet holes 12 on the main body 1. At the same time, the multi-ring liquid outlet holes 12 can still be expanded in number by corresponding one-to-one with the multi-ring baffle holes 21 on the liquid distribution baffle 2 through the cylindrical distribution cavity 130. Further, in this embodiment, the flow guide 6 is separately welded to the inner wall of the liner 1C on the liquid outlet side of the main body 1. This arrangement can further reduce the influence of the flow guide 6 on the processing of the multi-ring liquid outlet holes 12. However, this utility model does not impose any limitations on this. In other embodiments, the flow guide can also be integrally formed with the baffle located inside the liner. The baffle has multi-ring baffle holes that are coaxially corresponding to the multi-ring liquid outlet holes, but the diameter of the baffle holes is smaller than the outer diameter of the branch pipe insertion end to achieve the insertion limit of the branch pipe.

[0072] In this embodiment, as Figure 9 In this structure, the guide member 6 is a cylindrical sleeve. One end of the sleeve abuts against the liquid equalization baffle 2 region on the inner circumference of the multi-ring baffle holes 21, and the other end abuts against the liquid outlet end of the body 1 on the inner circumference of the multi-ring liquid outlet holes 12. Preferably, in this structure, the radial distance L1' from the outer peripheral wall of the sleeve (i.e., the guide member 6) to the inner edge of the innermost liquid outlet hole 12 satisfies: L1'≤4mm. The inner edge of the innermost liquid outlet hole refers to the intersection K of the line connecting the center of the innermost liquid outlet hole 12 and the center of the liquid outlet end of the body 1 with the edge of the innermost liquid outlet hole 12 on the liquid outlet end of the body 1.

[0073] However, this utility model does not impose any limitations on this. In other embodiments, the guide member 6 can also be a guide cone, with the bottom of the guide cone located at the liquid outlet end of the body 1 within the inner circumference of the multi-ring liquid outlet holes 12, and its end extending towards the liquid equalization baffle 2, such as... Figure 10 As shown.

[0074] The specific structures of the inlet pipe, the main body, the liquid equalization baffle, and the branch pipe are basically the same as those of Example 1 and their variations, and will not be described in detail here.

[0075] Example 3

[0076] This embodiment is basically the same as Embodiment 1 and its variations, except that the structure of the liquid equalization partition 2 is different.

[0077] In this embodiment, as Figure 11As shown, the projection area 22 on the liquid equalization baffle 2, opposite to the liquid inlet 11, protrudes into the distribution cavity 130 to form a mixing cavity 23 with its opening facing the liquid inlet 11. The mixing cavity 23 provides mixing space for the refrigerant during the maximum kinetic energy phase after refrigerant reflection, enhancing turbulence to promote gas-liquid two-phase mixing. Simultaneously, when the mass flow rate and velocity of the input refrigerant are large, the mixing cavity 23 can effectively reduce the impact of the reflection force on the input refrigerant, preventing refrigerant backflow to the liquid inlet 11 due to excessive reflection force.

[0078] like Figure 11 , Figure 12 as well as Figure 13 As shown, the mixing cavity 23 is a cylindrical cavity with a square longitudinal section profile, and the outer bottom surface of the mixing cavity 23 abuts against the inner bottom wall of the liquid outlet end of the body 1. Preferably, the radial distance L1 from the outer peripheral wall of the mixing cavity 23 to the inner edge of the innermost liquid outlet hole satisfies: L1≤4mm. The inner edge of the innermost liquid outlet hole refers to the intersection point K of the line connecting the center of the innermost liquid outlet hole 12 and the center of the liquid outlet end of the body 1 with the edge of the innermost liquid outlet hole 12 on the liquid outlet end of the body 1. However, this utility model does not impose any limitation on this.

[0079] Although this embodiment is described with the mixing cavity 23 abutting against the inner wall of the liquid outlet end of the main body 1 as an example, the present invention does not limit this in any way. In other embodiments, the outer bottom surface of the mixing cavity may not abut against the inner bottom wall of the liquid outlet end of the main body. Regarding the shape of the mixing cavity, in other embodiments, the mixing cavity may also be a prism with a square longitudinal section outline, a frustum of a cone with a trapezoidal longitudinal section outline, or a frustum of a pyramid (e.g., Figure 14 (As shown), a cone or pyramid with a triangular longitudinal section profile (such as...) Figure 15 (as shown) and combinations of partially circular longitudinal section profiles; such as combinations of cylindrical and partially spherical shapes (e.g.) Figure 16 (as shown), combinations of frustums and partial spheres, combinations of prisms and partial spheres, etc.

[0080] Although this embodiment is described using the example of the projection area 22 protruding into the distribution cavity 130 to form a mixing cavity 23 with its opening facing the liquid inlet hole 11, the present invention does not limit this in any way. In other embodiments, the projection area of ​​the liquid inlet hole on the partition plate may also protrude towards the side where the liquid inlet hole is located. The protrusion may be one or more combinations of a spherical bubble with a partially circular longitudinal section profile, a pyramid with a square longitudinal section profile, a frustum or truncated cone with a trapezoidal longitudinal section profile, or a cone or frustum with a triangular longitudinal section profile.

[0081] Similar to the plate-type liquid equalization baffle with nearly flat surfaces on both sides in Embodiment 1, the liquid equalization baffle structure provided in this embodiment can also be used with the flow guide in Embodiment 3, such as... Figure 17 As shown, a spacer serving as a flow guide 6 is added to the outside of the mixing cavity 23. Furthermore, in other embodiments, when the projection area of ​​the liquid inlet hole on the liquid equalization baffle protrudes towards one side of the liquid equalization baffle, a spacer or flow guide cone serving as a flow guide can also be provided in the distribution cavity.

[0082] Similarly, the specific structures of the inlet pipe, the main body, and the branch pipes are basically the same as those in Embodiment 1 and their variations, and will not be described in detail here.

[0083] Example 4

[0084] This embodiment is basically the same as Embodiment 1 and its variations, except that: Figure 18 As shown, in this embodiment, the liquid equalization assembly also includes a jetting element 7 disposed in the distribution cavity 130. A jetting hole 71 is formed on the jetting element 7 and the jetting hole 71 is opposite to the projection area 22 of the liquid inlet hole 11 on the liquid equalization partition 2.

[0085] In this embodiment, the refrigerant flow rate after being regulated by the liquid equalization baffle 2 is accelerated by adding a jet component 7 to form a secondary jet (the primary jet is the refrigerant acceleration at the jet section 52 on the liquid inlet pipe 5), so that the refrigerant can always maintain a uniformly mixed diffuse flow pattern during the redistribution process after regulation, thereby improving the distribution uniformity.

[0086] In this embodiment, the liquid equalization assembly also includes a reflective mixing guide plate 8 disposed in the distribution cavity 130 and located downstream of the jet member 7. The reflective mixing guide plate 8 has multiple rings of guide holes 81 that correspond one-to-one with the multiple liquid outlet holes 12 and are distributed in a ring array. The multiple rings of guide holes 81 are distributed on the outer peripheral plane of the projection area of ​​the jet hole 71 on the reflective mixing guide plate 8.

[0087] In this embodiment, the projection area of ​​the jet orifice 71 on the reflective mixing guide plate 8 protrudes towards the liquid outlet side of the body 1 to form a reflective mixing cavity 82 with its opening facing the jet orifice 71. The bottom wall of the reflective mixing cavity 82 reflects the refrigerant sprayed from the jet orifice 71. The reflected refrigerant violently collides within the reflective mixing cavity 82, further enhancing the turbulence of the two-phase flow to promote thorough mixing of the refrigerant. In this embodiment, the reflective mixing cavity 82 is a cylindrical chamber with a square longitudinal cross-sectional profile. However, this invention does not limit this. In other embodiments, the shape of the mixing cavity may also be one or more combinations of a prism with a square longitudinal cross-sectional profile, a frustum or truncated cone with a trapezoidal longitudinal cross-sectional profile, a cone or pyramid with a triangular longitudinal cross-sectional profile, and a partially circular longitudinal cross-sectional profile; such as a combination of a cylinder and a partially spherical shape, a combination of a frustum or a partially spherical shape, a combination of a prism and a partially spherical shape, etc.

[0088] Although this embodiment uses a reflective mixing cavity 82 formed on the reflective mixing plate 8 as an example, the present invention does not limit this in any way. In other embodiments, the downstream surface of the reflective mixing guide plate 8 can be set to be close to a plane, and the liquid equalization assembly also includes a guide member 6 disposed in the flow distribution cavity 130 and located downstream of the reflective mixing guide plate 8. The guide member 6 is located on the inner periphery of the multi-ring liquid outlet holes 12, and the guide member 6 and the peripheral wall of the body 1 form an annular flow channel connecting the multi-ring liquid outlet holes 12. Specifically, the guide member 6 can be a cylindrical spacer, one end of which abuts against the reflective mixing guide plate 8 region on the inner periphery of the multi-ring liquid outlet holes 81, and the other end abuts against the liquid outlet end of the body 1 on the inner periphery of the multi-ring liquid outlet holes 12, such as... Figure 19 As shown. Alternatively, the guide element 6 is a guide cone, with its bottom located at the liquid outlet end of the body 1 within the inner circumference of the multi-ring liquid outlet holes 12, and its end extending towards the reflective mixing guide plate 8, as shown. Figure 20 As shown.

[0089] Furthermore, in other embodiments, the downstream of the jet element 7 may not be provided with a reflective mixing guide plate, but only with a guide cone (i.e., guide element 6), such as... Figure 21 As shown.

[0090] although Figures 18 to 21 In this embodiment, the liquid equalization baffles 2 are all plate structures with flat surfaces on both sides. However, this utility model does not impose any limitations on this. In other embodiments, the projection area 22 of the liquid inlet hole 11 on the liquid equalization baffle 2 can be provided to protrude to one side of the liquid equalization baffle 2 to form a mixing cavity 23, such as... Figure 22 As shown.

[0091] Similarly, the specific structures of the inlet pipe, the main body, and the branch pipes are basically the same as those in Embodiment 1 and their variations, and will not be described in detail here.

[0092] Example 5

[0093] This embodiment is basically the same as Embodiment 4 and its variations, except that in this embodiment, the projection area 22 of the liquid inlet hole 11 on the liquid equalization baffle 2 protrudes towards the side where the jet component 7 is located to form a mixing cavity 23. The setting of the mixing cavity 23 on the liquid equalization baffle 2 allows the reflected refrigerant to participate in mixing with maximum kinetic energy, thereby increasing the turbulence of the two-phase flow. However, due to the limitations of the depth of the mixing cavity 23 and the inner diameter of the body 1, the volume of the flow pattern maintenance cavity 102 enclosed by the liquid equalization baffle 2 and the jet component 7 may be large. The initial diffuse flow formed after being regulated by the pre-rectification cavity 101 enclosed by the liquid equalization baffle 2 and the liquid inlet end of the body 1 is very likely to undergo gas-liquid two-phase separation again due to over-expansion after entering the excessively large flow pattern maintenance cavity 102.

[0094] To solve this problem, such as Figure 23 and Figure 24As shown, the liquid equalization assembly also includes a partition plate 9 disposed between the liquid equalization baffle 2 and the jetting element 7. The partition plate 9 divides the flow pattern maintaining cavity 102 enclosed by the liquid equalization baffle 2 and the jetting element 7 into a first maintaining cavity 1021 and a second maintaining cavity 1022. The partition plate 9 has multiple partition plate through holes 91 connecting the first maintaining cavity 1021 and the second maintaining cavity 1022. The volumes V1 of the pre-rectifying cavity 101, V21 of the first maintaining cavity 1021, and V22 of the second maintaining cavity 1022 satisfy the following values: 0.75 ≤ V1 / V21 ≤ 1.3, 0.75 ≤ V21 / V22 ≤ 1.3. The partition plate 9 precisely controls the expansion degree of the refrigerant when flowing through adjacent chambers, ensuring that the refrigerant develops into a stable diffused flow pattern after flowing through the first maintaining cavity 1021 and the second maintaining cavity 1022.

[0095] In this embodiment, as Figure 23 and Figure 24 As shown, a clearance hole 92 is formed on the partition plate 9 opposite to the mixing cavity 23, and the partition plate 9 is sleeved on the outer periphery of the mixing cavity 23 through the clearance hole 92. At this time, the pre-rectification cavity 101 refers to the cavity formed between the plane where the upstream surface of the liquid equalization partition plate 2 at the partition hole 21 is located and the inner wall of the liquid inlet end 11 of the body, as shown. Figure 23 The area indicated by the dashed line. The first maintaining cavity 1021 is an annular chamber surrounding the mixing cavity 23, enclosed by the downstream surface of the equalizing baffle 2 and the upstream surface of the partition plate 9, as shown in the figure. Figure 23 The area indicated by the dashed line. The second maintaining cavity 1022 is the chamber enclosed by the downstream surface of the equalizing baffle 2, the downstream surface of the partition plate 9, and the upstream surface of the jet component 7 at the mixing cavity 23, as shown below. Figure 23 The area indicated by the dashed line. However, this invention does not limit this area in any way.

[0096] In this embodiment, the multiple partition plate through holes 91 on the partition plate 9 are staggered with the multiple rings of partition plate holes 21 on the liquid equalization partition plate 2. This arrangement ensures that the refrigerant after initial rectification in the pre-rectification chamber 101 does not flow directly to the second maintenance chamber 1022, but instead, after mixing and developing in the first maintenance chamber 1021, it enters the second maintenance chamber 1022 through the multiple partition plate through holes 91 for further mixing and development.

[0097] Similar to Embodiment 4, in this embodiment, the liquid equalization assembly may further include a reflective mixing guide plate 8 and a guide plate 6 (e.g., downstream of the jet element 7) located downstream of the jet element 7. Figure 25 (As shown). However, this invention does not limit this in any way. In other embodiments, a reflective mixing guide plate may be provided downstream of the jet element, or only a guide cone as a guide element may be provided, or no component may be provided at all.

[0098] Similarly, the specific structures of the inlet pipe, the main body, and the branch pipes are basically the same as those in Embodiment 1 and their variations, and will not be described in detail here.

[0099] In summary, the liquid distribution assembly provided by this invention divides the internal cavity of the main body into two or more chambers through a liquid distribution baffle, providing space for refrigerant mixing and distribution while suppressing the problem of excessive refrigerant expansion caused by an excessively large cavity. The main body adopts a hollow cylindrical design, and its internal cavity cross-section and the multiple rings of baffle holes on the liquid distribution baffle are based on a circular topology optimization structure, which significantly improves the uniformity of distribution through geometric symmetry. This cylindrical structure forms a cylindrical distribution cavity with the liquid distribution baffle and the liquid outlet end of the main body. The multiple rings of liquid outlet holes can be distributed based on the one-to-one correspondence between the cylindrical distribution cavity and the multiple rings of baffle holes. While maintaining the radial dimension of the main body unchanged, the number of branch pipes can be increased several times compared to the traditional single-ring distribution scheme. By arranging multiple rings of baffle holes on the outer periphery of the liquid inlet projection area, the dynamic blocking and reflection of the input refrigerant by the projection area is used to enhance the mixing degree of the two-phase refrigerant. Combined with the staggered arrangement strategy of the multiple rings of baffle holes and the liquid inlet, the flow resistance of each baffle hole is balanced while preventing the refrigerant from flowing directly through, thus creating conditions for the refrigerant to be fully mixed before entering the multiple rings of baffle holes.

[0100] Although the present invention has been disclosed above by way of preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art may make some modifications and refinements without departing from the spirit and scope of the present invention. Therefore, the scope of protection of the present invention shall be determined by the scope of protection claimed in the claims.

Claims

1. A liquid homogenizing component, characterized in that, include: The main body is hollow and cylindrical, and has a liquid inlet, multiple liquid outlets, and a accommodating cavity; A liquid equalization baffle is arranged in the accommodating cavity along the axial direction perpendicular to the body. A distribution cavity is formed between the liquid equalization baffle and the liquid outlet end of the body, which connects multiple liquid outlet holes. The liquid equalization baffle is arranged radially with multiple rings of baffle holes arranged in a ring array around the axis of the body, and the multiple rings of baffle holes are located on the outer peripheral plane of the projection area of ​​the liquid inlet hole on the liquid equalization baffle. Multiple liquid outlet holes form multiple rings along the circumference of the body. Each ring of liquid outlet holes is distributed one-to-one with the partition holes on the corresponding ring through the distribution cavity. Multiple branch pipes are welded into the corresponding liquid outlet holes.

2. The liquid equalization component according to claim 1, characterized in that, Multiple septum holes on each ring are evenly spaced with equal center distances, and the center distance between two adjacent septum holes on the i-th ring is L. i The center distance between two adjacent diaphragm holes on the j-th ring is L. j The difference in center distance between any two rings of diaphragm holes is ΔL ij =∣L i -L j |≤1.2mm.

3. The liquid equalization component according to claim 1, characterized in that, At least a portion of the branch pipe has a bend near the liquid outlet end of the main body. When the bend angle at the bend is greater than or equal to 10 degrees, the length L of the straight pipe section between the upstream end of the bend and the end of the branch pipe inserted into the liquid outlet hole is ≥8mm.

4. The liquid equalization component according to claim 3, characterized in that, The liquid equalization assembly also includes a straight pipe sleeve that is fitted over the straight pipe section and inserted into the liquid outlet hole. The bend on the branch pipe is located at the downstream end of the straight pipe sleeve. The length of the straight pipe section is determined based on the straight pipe sleeve when the bend is formed.

5. The liquid equalization component according to claim 1, characterized in that, The partition holes are through holes or flanged holes extending into the distribution cavity, and the diameter of the partition holes is basically the same or gradually decreases along their extension direction. Alternatively, the baffle hole is an arc bubble hole whose hole wall protrudes arc-shaped towards one or both sides of the liquid equalization baffle.

6. The liquid equalization component according to claim 1, characterized in that, The liquid equalization baffle is a plate structure with both sides being nearly planar; Alternatively, the projection area of ​​the liquid inlet hole on the liquid equalization plate protrudes to one side of the liquid equalization plate, and the longitudinal cross-sectional outline of the protrusion is one or more combinations of square, trapezoidal, triangular or partially circular.

7. The liquid equalization component according to claim 1, characterized in that, The liquid equalization assembly also includes a flow guide disposed in the distribution chamber and located on the inner periphery of the multiple liquid outlet holes, wherein the flow guide and the peripheral wall of the body form an annular flow channel connecting the multiple liquid outlet holes.

8. The liquid equalization component according to claim 7, characterized in that, The flow guide is a cylindrical sleeve, with one end abutting the liquid equalization baffle area on the inner circumference of the multi-ring baffle holes, and the other end abutting the liquid outlet end of the body on the inner circumference of the multi-ring liquid outlet holes; or, the flow guide is a flow guide cone, with the bottom of the flow guide cone located at the liquid outlet end of the body on the inner circumference of the multi-ring liquid outlet holes, and its end extending toward the liquid equalization baffle.

9. The liquid equalization component according to claim 6 or 8, characterized in that, The projection area of ​​the liquid inlet hole on the liquid equalization baffle protrudes into the distribution cavity and abuts against the inner wall of the liquid outlet end of the body to form a mixing cavity; the radial distance L1 from the outer peripheral wall of the mixing cavity to the inner edge of the innermost liquid outlet hole satisfies: L1≤4mm; Alternatively, the radial distance L1 from the outer peripheral wall of the diaphragm to the inner edge of the innermost liquid outlet hole satisfies: L1≤4mm; The inner edge of the innermost liquid outlet refers to the intersection of the line connecting the center of the innermost liquid outlet and the center of the liquid outlet of the main body with the edge of the innermost liquid outlet on the liquid outlet end of the main body.

10. The liquid equalization component according to claim 1, characterized in that, The liquid equalization assembly also includes a jetting element disposed in the distribution chamber, wherein a jetting hole is formed on the jetting element and the projection area of ​​the jetting hole and the liquid inlet hole on the liquid equalization partition is opposite.

11. The liquid equalization component according to claim 10, characterized in that, The liquid equalization component also includes a reflective mixing guide plate disposed in the distribution cavity and located downstream of the jet component. The reflective mixing guide plate has multiple rings of guide holes that correspond one-to-one with multiple liquid outlet holes and are distributed in a ring array. The multiple rings of guide holes are distributed on the outer peripheral plane of the projection area of ​​the jet holes on the reflective mixing guide plate. Alternatively, the liquid equalization assembly may further include a flow guide placed in the distribution chamber and downstream of the jet component. The flow guide is located on the inner circumference of the multiple liquid outlet holes, and the flow guide and the peripheral wall of the body form an annular flow channel connecting the multiple liquid outlet holes.

12. The liquid equalization component according to claim 10, characterized in that, When the projection area of ​​the liquid inlet on the liquid equalization baffle protrudes towards the side where the jet is located, the liquid equalization assembly further includes a partition plate disposed between the liquid equalization baffle and the jet. The partition plate divides the flow pattern maintenance cavity enclosed by the liquid equalization baffle and the jet into a first maintenance cavity and a second maintenance cavity. The partition plate is formed with a plurality of partition plate through holes connecting the first maintenance cavity and the second maintenance cavity. The pre-rectification cavity volume V1, the first maintenance cavity volume V21, and the second maintenance cavity volume V22 enclosed between the liquid equalization baffle and the liquid inlet end of the body satisfy the following: 0.75≤V1 / V21≤1.3, 0.75≤V21 / V22≤1.

3.

13. The liquid equalization component according to claim 1, characterized in that, The liquid equalization assembly also includes a liquid inlet pipe welded to the liquid inlet hole. The liquid inlet pipe has a main body section with a basically unchanged inner diameter and a jet section located downstream of the main body section with a smaller inner diameter than the main body section. The jet section is a straight section with a smaller inner diameter than the main body section or a Venturi tube section with a jet throat.

14. The liquid equalization component according to claim 1, characterized in that, The branch pipe is an integral pipe fitting with a basically uniform inner diameter; or, the branch pipe includes a connecting section and a branch pipe extension section, and the inner diameter of the connecting section is greater than or equal to the inner diameter of the branch pipe extension section.

15. A heat exchanger, characterized in that, Includes the liquid homogenizing component as described in claim 1.

16. The heat exchanger according to claim 15, characterized in that, The heat exchanger is a shell-and-tube heat exchanger, and the multiple branch pipes on the liquid equalization assembly are respectively assembled one-to-one with the multiple heat exchange tubes on the shell-and-tube heat exchanger.

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