Refrigerant distribution assembly for shell and tube heat exchanger, shell and tube heat exchanger and refrigeration equipment

Abstract

The invention provides a refrigerant distribution assembly for a shell and tube heat exchanger, the shell and tube heat exchanger and refrigeration equipment. The refrigerant distribution assembly for the shell and tube heat exchanger comprises a distributor and a branch pipe adapter plate. A liquid uniformizing partition plate in the distributor is arranged in a containing cavity of a distribution body in the axial direction perpendicular to the distribution body, a distribution cavity is defined by the liquid uniformizing partition plate and the liquid outlet end of the distribution body, and multiple circles of partition plate holes distributed around the axis of the distribution body in an annular array mode are formed in the liquid uniformizing partition plate in the radial direction. The multiple circles of partition plate holes are located in the peripheral plane of the projection area of the liquid inlet holes in the liquid uniformizing partition plate. The plurality of distribution holes form a plurality of circles of annular columns along the circumferential direction of the distribution body and are distributed in one-to-one correspondence with the partition plate holes in the corresponding circles, and the plurality of branch pipes are respectively welded in the corresponding distribution holes. The branch pipe adapter plate is arranged at the tail ends of the branch pipes, a plurality of adapter positioning holes which are in one-to-one correspondence with ports of heat exchange pipes in the shell and tube heat exchanger and are distributed in rows and columns are formed in the branch pipe adapter plate, and the tail end of each branch pipe is inserted into the corresponding adapter positioning hole.

Description

Technical Field

[0001] The present invention relates to the field of refrigeration fittings, and particularly to a refrigerant distribution assembly for a shell-and-tube heat exchanger, a shell-and-tube heat exchanger, and a refrigeration device. Background Art

[0002] A shell-and-tube heat exchanger is a surface heat exchanger with the tube wall surface enclosed in a shell as the heat transfer surface. Its core components include a shell, a tube bundle, a tube sheet, a baffle plate, and a tube box. Heat exchange is achieved through the tube-side medium (flowing inside the tubes) and the shell-side medium (flowing outside the tubes). To improve the heat exchange efficiency, existing shell-and-tube heat exchangers generally adopt a multi-pass and multi-tube structure. During operation, the tube-side medium needs to be evenly distributed to each heat exchange tube. In a dry heat exchanger, the tube-side medium is a refrigerant in a gas-liquid two-phase mixture. When the two-phase flow refrigerant enters the tube box, gas-liquid separation occurs due to the superposition of gravity and expansion effects, and it is difficult to evenly distribute the liquid refrigerant to each heat exchange tube. Especially when the two-phase flow refrigerant impacts the tube sheet at high speed, it will also cause intense turbulence, vortices, and foam phenomena, exacerbating the uneven distribution problem. This uneven distribution of the orifice plate structure not only reduces the heat exchange efficiency but may also cause compressor damage because excessive liquid refrigerant in some heat exchange tubes is not completely evaporated, and the evaporated gaseous refrigerant carries liquid droplets into the compressor.

[0003] To improve the uniformity of refrigerant distribution, some people have also proposed a shell-and-tube heat exchanger with a distributor. The distributor in this structure is an integral conical distributor made of copper material. The conical distributor accelerates through the throat to promote the mixing of the two-phase flow and then evenly distributes the refrigerant into the annular inclined flow channels that are annularly distributed around the shunt cone and are all connected to the throat. However, limited by the spatial layout of the conical structure and the annular inclined flow channels, the branch pipes on this type of distributor can only be distributed in a single-ring annular array at the liquid outlet end of the distributor. The increase in the number of branch pipes will cause a sharp increase in the geometric size of the distribution body. This will not only significantly increase the material cost of the distributor but also cause an adaptation obstacle due to the limitation of the tube sheet size of the existing shell-and-tube heat exchanger and is difficult to apply. In addition, some people have also proposed a tube-type distributor. This scheme realizes the distribution of the refrigerant by opening a liquid inlet pipe 601 and a plurality of 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, and the refrigerant will preferentially enter the corresponding heat exchange tube through the distribution hole with a short flow channel, resulting in an imbalance in the distribution of the two-phase refrigerant. The superposition of gravity and refrigerant expansion will further exacerbate the uneven distribution problem. Moreover, the evaporator structure proposed in Chinese Patent CN117387254A, which sets a partition plate and a gaseous refrigerant distribution pipe in the tube box, adopts a gas-liquid separation design for refrigerant distribution. However, its core gaseous refrigerant distribution pipe still uses Figure 1This tubular distributor has the inherent defect of unequal flow channel spacing, which causes uneven distribution of gaseous refrigerant and makes it impossible to evenly tear the liquid refrigerant. At the same time, the separated liquid refrigerant is deposited at the bottom of the liquid refrigerant distribution cavity under the action of gravity due to the attenuation of flow velocity, causing imbalance in the secondary distribution of liquid refrigerant. In addition, the design of gas-liquid separation and impact mixing will also bring problems such as increased complexity and soaring manufacturing costs.

[0004] Furthermore, in traditional shell and tube heat exchangers, heat exchange tubes are usually arranged in a compact matrix, that is, multiple heat exchange tubes are regularly arranged on the tube sheet surface in a staggered manner of horizontal and vertical rows and columns. The branch pipes on the distributor are distributed in a circular ring shape. This annular distribution is misaligned with the matrix arrangement of the heat exchange tubes in the spatial topological structure. The end position of the branch pipe cannot correspond to the inlet position of the corresponding heat exchange tube. During installation, the position of the end of each branch pipe needs to be adjusted one by one to adapt to the corresponding inlet position of the heat exchange tube. This operation method of correcting each branch pipe one by one is not only difficult and inefficient, but also requires precise spatial positioning measurement. It will also limit the operating space due to the close spacing between the pipes, which can easily cause deformation of the branch pipe or sealing failure. Summary of the invention

[0005] In order to overcome the deficiencies of the prior art, the present invention provides a refrigerant distribution assembly for a shell and tube heat exchanger, a shell and tube heat exchanger and a refrigeration device.

[0006] In order to achieve the above-mentioned purpose, the present invention provides a refrigerant distribution assembly for a shell and tube heat exchanger, which includes a distributor and a branch pipe adapter plate. The distributor includes a distribution body, a liquid equalizing baffle and a plurality of branch pipes. The distribution body is in a hollow columnar shape and has a liquid inlet hole, a plurality of distribution holes and a receiving cavity; the liquid equalizing baffle is arranged in the receiving cavity along an axial direction perpendicular to the distribution body, and a distribution cavity connecting a plurality of distribution holes is formed between the liquid equalizing baffle and the liquid outlet end of the distribution body. A plurality of baffle holes distributed in a circular array around the axis of the distribution body are arranged radially on the liquid equalizing baffle, and the plurality of baffle holes are located on the outer peripheral plane of the projection area of ​​the liquid inlet hole on the liquid equalizing baffle; the plurality of distribution holes form a plurality of annular rows along the circumference of the distribution body, and each circle of distribution holes is distributed one-to-one with the baffle holes on the corresponding circle through the distribution cavity, and the plurality of branch pipes are respectively welded in the corresponding distribution holes. A branch pipe adapter plate is arranged at the end of multiple branch pipes. A plurality of adapter positioning holes are formed on the branch pipe adapter plate for fixing the multiple branch pipes and corresponding to the ports of the heat exchange pipes in the shell and tube heat exchanger in a matrix. The end of each branch pipe is inserted into the corresponding adapter positioning hole to assemble the corresponding heat exchange pipe in the shell and tube heat exchanger.

[0007] In one embodiment of the present invention, on the branch pipe adapter plate, at least a portion of the adapter positioning holes have a diameter larger than the outer diameter of the branch pipe assembled therewith.

[0008] In an embodiment of the present invention, the peripheral wall at the end of each branch pipe is hermetically welded within the transfer positioning hole, and the end of each branch pipe serves as a connection end to be sleeved and inserted into the corresponding heat exchange pipe within the shell-and-tube heat exchanger.

[0009] In an embodiment of the present invention, when the aperture of the transfer positioning hole is larger than the outer diameter of the corresponding branch pipe, the branch pipe transfer plate further includes an adjustment bushing sleeved on the outer peripheral wall of the branch pipe and inserted into the transfer positioning hole, and the branch pipe is hermetically welded within the transfer positioning hole through the adjustment bushing.

[0010] In an embodiment of the present invention, each branch pipe is limited within the transfer positioning hole, and its end extends out of the transfer positioning hole to form a connection end for welding and connecting the corresponding heat exchange pipe within the shell-and-tube heat exchanger.

[0011] In an embodiment of the present invention, the multiple partition holes in each circle are evenly spaced at equal center distances. The center distance between two adjacent partition holes in the i-th circle is L i , and the center distance between two adjacent partition holes in the j-th circle is L j , and the difference △L ij in the center distances of the partition holes between any two circles i = ∣L j - L

[0012] In an embodiment of the present invention, on the side of the branch pipe transfer plate close to the distribution body, at least a part of the branch pipes are formed with bending parts. When the bending angle at the bending part is greater than or equal to 10 degrees, the length L of the straight pipe section between the upstream end of the bending part and the inner end of the branch pipe inserted into the distribution hole is ≥ 8 mm.

[0013] In an embodiment of the present invention, the distributor further includes a straight pipe sleeve sleeved on the straight pipe section and inserted into the distribution hole. The bending part on the branch pipe is located at the downstream end of the straight pipe sleeve, and the length of the straight pipe section is determined based on the straight pipe sleeve when forming the bending part.

[0014] In an embodiment of the present invention, the partition hole is a through hole or a flanging hole extending towards the distribution cavity, and the apertures of the partition holes are basically the same or gradually decrease along their extending directions;

[0015] Alternatively, the partition hole is an arc bubble hole with the hole wall arcuately protruding towards one or both sides of the liquid distribution partition.

[0016] In an embodiment of the present invention, the liquid distribution partition is a plate body structure with both sides being close to planar; or, the projection area of the liquid inlet hole on the liquid distribution partition protrudes towards one side of the liquid distribution partition, and the shape of the longitudinal section contour line of the protrusion is one or a combination of a square, a trapezoid, a triangle, or a partial circle.

[0017] In an embodiment of the present invention, the dispenser further includes a flow guiding member disposed in the dispensing cavity and located on the inner circumference of the multi-loop dispensing holes. An annular flow channel communicating with the multi-loop dispensing holes is defined between the flow guiding member and the peripheral wall of the dispensing body.

[0018] In an embodiment of the present invention, the flow guiding member is a cylindrical spacer sleeve. One end of the spacer sleeve abuts against the liquid equalizing partition region on the inner circumference of the multi-loop partition holes, and the other end thereof abuts against the liquid outlet end of the dispensing body on the inner circumference of the multi-loop dispensing holes.

[0019] Alternatively, the flow guiding member is a flow guiding cone. The bottom of the flow guiding cone is disposed at the liquid outlet end of the dispensing body on the inner circumference of the multi-loop dispensing holes, and its end extends towards the liquid equalizing partition.

[0020] In an embodiment of the present invention, the projection area of the liquid inlet hole on the liquid equalizing partition bulges towards the dispensing cavity and abuts against the liquid outlet end of the dispensing body to form a mixing concave cavity. The radial distance L1 from the outer peripheral wall of the mixing concave cavity to the inner edge of the innermost loop of dispensing holes satisfies: L1 ≤ 4 mm.

[0021] Alternatively, the radial distance L1' from the outer peripheral wall of the spacer sleeve to the inner edge of the innermost loop of dispensing holes satisfies: L1' ≤ 4 mm.

[0022] The inner edge of the innermost loop of dispensing holes refers to: at the liquid outlet end of the dispensing body, the intersection of the connection line between the center of the innermost loop of dispensing holes and the center of the liquid outlet end of the dispensing body and the edge of the innermost loop of dispensing holes.

[0023] In an embodiment of the present invention, the dispenser further includes a jet member disposed in the dispensing cavity. A jet hole is formed on the jet member, and the jet hole is opposite to the projection area of the liquid inlet hole on the liquid equalizing partition.

[0024] In an embodiment of the present invention, the dispenser further includes a reflection mixing and flow guiding plate disposed in the dispensing cavity and located downstream of the jet member. The reflection mixing and flow guiding plate has multi-loop flow guiding holes corresponding to the plurality of dispensing holes one by one and distributed in an annular array. The multi-loop flow guiding holes are distributed on the outer peripheral plane of the projection area of the jet hole on the reflection mixing and flow guiding plate.

[0025] Alternatively, the dispenser further includes a flow guiding member disposed in the dispensing cavity and located downstream of the jet member. The flow guiding member is located on the inner circumference of the multi-loop dispensing holes. An annular flow channel communicating with the multi-loop dispensing holes is defined between the flow guiding member and the peripheral wall of the dispensing body.

[0026] In an embodiment of the present invention, when the projection area of the liquid inlet hole on the liquid distribution partition bulges towards the side where the jet member is located, the distributor further includes a partition plate disposed between the liquid distribution partition and the jet member. The partition plate divides the flow pattern maintenance cavity formed by enclosing the liquid distribution partition and the jet member into a first maintenance cavity and a second maintenance cavity. A plurality of partition plate through holes communicating the first maintenance cavity and the second maintenance cavity are formed on the partition plate; wherein, the volume V1 of the pre-rectification cavity formed by enclosing the liquid distribution partition and the liquid inlet end of the distribution body, the volume V21 of the first maintenance cavity, and the volume V22 of the second maintenance cavity satisfy: 0.75 ≤ V1 / V21 ≤ 1.3, 0.75 ≤ V21 / V22 ≤ 1.3.

[0027] In an embodiment of the present invention, the distributor further includes a liquid inlet pipe welded to the liquid inlet hole. The liquid inlet pipe has a main body section with a substantially constant inner diameter and a jet section located downstream of the main body section and having a relatively reduced inner diameter compared to the main body section. The jet section is a straight section with a relatively reduced inner diameter compared to the main body section or a Venturi tube section with a jet throat.

[0028] In an embodiment of the present invention, the branch pipe is an integral pipe fitting with a substantially consistent inner diameter; or, the branch pipe includes a connecting pipe section and a branch pipe extension section, and the inner diameter of the connecting pipe section is greater than or equal to the inner diameter of the branch pipe extension section.

[0029] On the other hand, the present invention also provides a shell-and-tube heat exchanger, which includes a heat exchanger housing and a tube-side component disposed inside the heat exchanger housing. The tube-side component includes a plurality of heat exchange tubes and a refrigerant distribution component for the shell-and-tube heat exchanger. The multiple branch pipes on the distributor are respectively hermetically connected to the multiple heat exchange tubes through a branch pipe adapter plate.

[0030] In an embodiment of another aspect of the present invention, the tube-side component further includes a tube sheet. The multiple heat exchange tubes are sequentially assembled into a plurality of tube sheet assembly holes arranged in rows and columns on the tube sheet. A tube box is formed between the tube sheet and the end cover of the heat exchanger housing. The branch pipe adapter plate is disposed inside the tube box, and its outer periphery is hermetically welded to the tube sheet to form a sealed cavity therebetween. The peripheral wall of each branch pipe is hermetically welded in the transfer positioning hole, and the end of each branch pipe is inserted into the corresponding heat exchange tube on the tube sheet assembly hole at the sealed cavity.

[0031] In an embodiment of another aspect of the present invention, each branch pipe is limited in the transfer positioning hole, and its end extends out of the transfer positioning hole and is hermetically connected to the corresponding heat exchange tube by welding.

[0032] In an embodiment of another aspect of the present invention, the distribution body is arranged inside the heat exchanger housing along a direction substantially parallel to the axial direction of the heat exchanger housing;

[0033] Alternatively, the distribution body is disposed inside the heat exchanger housing along a direction substantially perpendicular to the axial direction of the heat exchanger housing, and each branch pipe is bent so that its end is inserted into the transfer positioning hole on the branch pipe adapter plate.

[0034] In an embodiment of another aspect of the present invention, the heat exchange tubes are U-shaped tube bundles, and the tube-side assembly includes a plurality of refrigerant distribution assemblies for shell-and-tube heat exchangers disposed at the same end of the heat exchanger housing.

[0035] Alternatively, the heat exchange tubes are straight tube bundles, and the tube-side assembly includes a refrigerant distribution assembly for a shell-and-tube heat exchanger disposed at one end of the heat exchanger housing and another refrigerant distribution assembly for a shell-and-tube heat exchanger disposed at the other end of the heat exchanger housing.

[0036] On the other hand, the present invention further provides a refrigeration device including the above-mentioned shell-and-tube heat exchanger.

[0037] In summary, the refrigerant distribution assembly for the shell-and-tube heat exchanger provided by the present invention divides the accommodation cavity in the distribution body into two or more chambers through a liquid distribution partition, while providing a space for refrigerant mixing and distribution, suppressing the problem of excessive refrigerant expansion caused by an overly large cavity. The distribution body adopts a hollow columnar design, and the cross-section of its inner cavity and the multi-ring partition holes on the liquid distribution partition are both based on a circular topology optimization structure, significantly improving the distribution uniformity through geometric symmetry. This columnar structure forms a columnar distribution cavity between the liquid distribution partition and the liquid outlet end of the distribution body, and the multi-ring distribution holes can be distributed in one-to-one correspondence with the multi-ring partition holes based on the columnar distribution cavity. Under the condition of keeping the radial dimension of the distribution body unchanged, the number of branch pipes can be increased several times compared with the traditional single-ring annular distribution scheme. By arranging the multi-ring partition holes on the peripheral plane of the projection area of the liquid inlet hole, the dynamic blocking and reflection of the input refrigerant by the projection area are used to strengthen the mixing degree of the two-phase refrigerant. Combining the staggered arrangement strategy of the multi-ring partition holes and the liquid inlet hole, while balancing the flow resistance of each partition hole channel, it can also prevent the refrigerant from passing through directly, creating conditions for the full mixing of the refrigerant before entering the multi-ring partition holes.

[0038] Furthermore, by providing a branch pipe adapter plate at the end of the branch pipe, using its transfer positioning holes distributed in a determinant pattern, the end positions of the multi-ring branch pipes distributed in an annular array on the distributor are uniformly converted into a determinant distribution adapted to the ports of the heat exchange tubes, realizing the conversion of the spatial topology structure of the connection end of the refrigerant distribution assembly. At the same time, the transfer positioning holes also achieve precise positioning of the end position of each branch pipe; during assembly, multiple branch pipes and heat exchange tubes can be assembled at one time through the branch pipe adapter plate, improving the assembly efficiency and reducing the assembly difficulty.

[0039] To make the above and other objects, features, and advantages of the present invention more obvious and understandable, the following specifically enumerates preferred embodiments and, in conjunction with the accompanying drawings, provides a detailed description as follows. Description of the Drawings

[0040] Figure 1 The figure shows a structural schematic diagram of an existing tube distributor.

[0041] Figure 2 The figure shows a structural schematic diagram of the refrigerant distribution assembly for the shell-and-tube heat exchanger provided in Embodiment 1 of the present invention.

[0042] Figure 2A Shown is Figure 2 the assembly schematic diagram of the distribution body and the liquid inlet pipe in

[0043] Figure 3 Shown is Figure 2 the enlarged schematic diagram at position A in

[0044] Figure 4 Shown is Figure 2 the enlarged schematic diagram at position B in

[0045] Figure 5 Shown is Figure 2 the structural schematic diagram after removing part of the branch pipes.

[0046] Figure 6 Shown is Figure 5 the enlarged schematic diagram at position C in

[0047] Figure 7 Shown is Figure 2 the structural schematic diagram of the branch pipe adapter plate in

[0048] Figure 8 Shown is Figure 2 the structural schematic diagram of the liquid equalizing partition plate in

[0049] Figure 9 Shown is Figure 8 the projection schematic diagram of

[0050] Figure 10 and Figure 11 the partial schematic diagram of the refrigerant distribution component for the shell-and-tube heat exchanger provided by another embodiment of the present invention.

[0051] Figure 12 Shown is the structural schematic diagram of the inner shell-side component of the shell-and-tube heat exchanger provided by Embodiment 1 of the present invention.

[0052] Figure 13 is Figure 12 the enlarged schematic diagram at position E in

[0053] Figure 14A 、 Figure 14B and Figure 14C Shown is the structural schematic diagram of the inner shell-side component of the shell-and-tube heat exchanger provided by another embodiment of the present invention..

[0054] Figure 15 Shown is the structural schematic diagram of the refrigerant distribution component for the shell-and-tube heat exchanger provided by Embodiment 2 of the present invention.

[0055] Figure 16 Shown is Figure 15 the enlarged schematic diagram at position D in

[0056] Figure 17 The figure shows a schematic structural diagram of an inner shell-side component of a shell-and-tube heat exchanger provided by another embodiment of the present invention.

[0057] Figure 18 As shown in Figure 17 an enlarged schematic view of the position F in

[0058] Figure 19 The figure shows a partial schematic diagram of a refrigerant distribution component for a shell-and-tube heat exchanger provided by Embodiment III of the present invention.

[0059] Figure 20 The figure shows a partial schematic diagram of a shell-and-tube heat exchanger provided by another embodiment of the present invention.

[0060] Figure 21 The figure shows a schematic structural diagram of a refrigerant distribution component for a shell-and-tube heat exchanger provided by Embodiment IV of the present invention.

[0061] Figure 22 As shown in Figure 21 a schematic structural diagram of the liquid distribution baffle in

[0062] Figure 23 is Figure 22 a sectional view of

[0063] Figure 24 , Figure 25 and Figure 26 are schematic structural diagrams of the liquid distribution baffle in a refrigerant distribution component for a shell-and-tube heat exchanger provided by another embodiment of the present invention.

[0064] Figure 27 The figure shows a partial schematic diagram of a refrigerant distribution component for a shell-and-tube heat exchanger provided by another embodiment of the present invention.

[0065] Figure 28 The figure shows a partial schematic diagram of a refrigerant distribution component for a shell-and-tube heat exchanger provided by Embodiment V of the present invention.

[0066] Figure 29 , Figure 30 , Figure 30 , Figure 31 and Figure 32 The figure shows a partial schematic diagram of a refrigerant distribution component for a shell-and-tube heat exchanger provided by another embodiment of the present invention.

[0067] Figure 33 The figure shows a partial schematic diagram of a refrigerant distribution component for a shell-and-tube heat exchanger provided by Embodiment VI of the present invention.

[0068] Figure 34 As shown in Figure 33 a schematic structural diagram of the partition baffle in

[0069] Figure 35 The figure shows a partial schematic view of a refrigerant distribution assembly for a shell-and-tube heat exchanger provided by another embodiment of the present invention. Detailed implementation manners

[0070] In this application, the downstream or upstream is divided based on the flow direction of the refrigerant. Generally, the refrigerant flows from the upstream to the downstream, and the area located downstream receives the refrigerant from the upstream. When the distributor is installed vertically or obliquely, the liquid inlet hole of the distributor is located below the liquid outlet hole along the direction of gravity, and the inertial force of the refrigerant in the distributor overcomes the gravity and flows in the direction opposite to the gravity; at this time, the upstream and downstream are still divided according to the flow direction of the refrigerant.

[0071] Embodiment 1

[0072] In an existing shell-and-tube heat exchanger, the two-phase refrigerant directly enters the header and is then directly distributed into multiple heat exchange tubes connected to the tube sheet. This refrigerant distribution method with an orifice plate structure not only has low heat exchange efficiency but also there is a risk of liquid carryover in the compressor suction due to incomplete evaporation of the liquid refrigerant in some heat exchange tubes. To solve this problem, a solution of introducing a distributor into the shell-and-tube heat exchanger has been proposed. However, this technology has multiple technical bottlenecks: the conical distributor is difficult to expand the branch pipes due to space limitations and cannot be adapted to heat exchangers with a large number of tubes; the tube-type distributor (as shown in Figure 1 ) causes distribution imbalance due to unequal flow path distances; the gas-liquid separation type distributor not only inherits the defects of the tube-type distributor but also has a complex structure. At the same time, there is a spatial topological misalignment between the row arrangement of the heat exchange tubes and the circular arrangement of the branch pipes. When assembling, it is necessary to calibrate the end positions of the branch pipes one by one, which is not only difficult to assemble but also easily causes deformation or sealing failure.

[0073] In view of this, the present invention provides a refrigerant distribution assembly for a shell-and-tube heat exchanger with excellent distribution performance, the number of branch pipes can be adapted to heat exchange tubes of different specifications, and the assembly is convenient. As shown in Figures 2 to 9As shown, the refrigerant distribution assembly 220 for the shell and tube heat exchanger provided in this embodiment includes a distributor 10 and a branch pipe adapter plate 20. The distributor 10 includes a distribution body 1, a liquid equalizing baffle 2 and a plurality of branch pipes 3. The distribution body 1 is in a hollow columnar shape and has a liquid inlet hole 11, a plurality of distribution holes 12 and a receiving chamber 13. The liquid equalizing baffle 2 is arranged in the receiving chamber 13 along an axial direction perpendicular to the distribution body 1. A distribution chamber 130 connecting the plurality of distribution holes 12 is formed between the liquid equalizing baffle 2 and the liquid outlet end of the distribution body 1. A plurality of baffle holes 21 distributed in a circular array around the axis of the distribution body 1 are radially arranged on the liquid equalizing baffle 2, and the plurality of baffle holes 21 are located on the outer peripheral plane of the projection area 22 of the liquid inlet hole 11 on the liquid equalizing baffle 2. The plurality of distribution holes 12 form a plurality of annular rows along the circumference of the distribution body 1, and each circle of distribution holes 12 is distributed one-to-one with the partition holes 21 on the corresponding circle through the distribution cavity 130, and the plurality of branch pipes 3 are respectively welded in the corresponding distribution holes 12. The branch pipe adapter plate 20 is arranged at the ends of the plurality of branch pipes 3, and the branch pipe adapter plate 20 is formed with a plurality of transfer positioning holes 201 for fixing the plurality of branch pipes 3 and corresponding one-to-one with the heat exchange pipe ports in the shell and tube heat exchanger and distributed in a determinant manner, and the end of each branch pipe 3 is inserted into the corresponding transfer positioning hole 201 to assemble the corresponding heat exchange pipe in the shell and tube heat exchanger.

[0074] For multiple circles of distribution holes 12: Preferably, each distribution hole 12 is coaxially aligned with the corresponding partition hole 21 through a cylindrical distribution cavity 130. However, the present invention does not impose any limitation on this. In other embodiments, there may be a certain distance between the distribution hole axis and the partition hole axis. Further preferably, in this embodiment, the aperture of each partition hole 21 is substantially close to the aperture of the corresponding distribution hole 12. However, the present invention does not impose any limitation on this. In other embodiments, the aperture of the partition hole may be larger or smaller than the aperture of the corresponding distribution hole.

[0075] The refrigerant distribution assembly for the shell and tube heat exchanger provided in this embodiment uses a liquid-equalizing baffle 2 to divide the accommodating cavity 13 in the distribution body 1 into a dual-function chamber for mixing and distribution, which not only provides space for refrigerant mixing, but also effectively suppresses excessive expansion of the refrigerant by limiting the cavity volume. On this basis, a multi-circle annular array design is performed for the baffle holes 21 based on the circular inner cavity cross-section of the columnar distribution body 1; and the multi-circle baffle holes 21 form a one-to-one spatial mapping relationship with the multi-circle distribution holes 12 on the liquid outlet end of the distribution body 1 through the columnar distribution cavity 130. This layout enables the distributor provided in this embodiment to achieve a doubling of the number of branch pipes 3 while maintaining the radial size of the distribution body 1 unchanged, effectively solving the problem that the existing distributor is difficult to adapt to multiple heat exchange tubes on the shell and tube heat exchanger due to the limited number of branch pipes 3. Furthermore, on the liquid-distributing partition 2, by arranging the partition 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, strengthen the mixing of the gas-liquid two-phase refrigerant, and reorganize the refrigerant flow pattern to develop it into a fully mixed diffuse flow pattern to improve the distribution uniformity. At the same time, the staggered arrangement of multiple circles of partition holes 21 and the liquid inlet holes 11 not only achieves the balance of the flow path of each partition hole 21, but also effectively avoids the refrigerant from directly passing into the distribution chamber 130 before mixing, providing conditions for the two-phase refrigerant to be fully mixed and then distributed.

[0076] Furthermore, in order to solve the problem of difficult assembly of multiple branch pipes 3 on the distributor and multiple heat exchange tubes on the shell and tube heat exchanger, the branch pipe adapter plate 20 is provided at the end of the branch pipe 3 of the distributor 10 in this embodiment. The end position structure of the multiple rings of branch pipes 3 distributed in a circular ring is converted into a determinant topological structure adapted to the heat exchange tube by using multiple transfer positioning holes 201 distributed in rows and columns on the branch pipe adapter plate 20. This setting not only realizes the conversion and precise positioning of the end position of each branch pipe 3, but also enables multiple branch pipes 3 and heat exchange tubes to be assembled at one time through the branch pipe adapter plate 20, which significantly improves the assembly efficiency and reduces the difficulty of installation.

[0077] For the transfer positioning hole 201, its ideal aperture is generally close to the outer diameter of the corresponding branch pipe 3 to achieve socket assembly or sealed welding, that is, it is basically close to equal-diameter assembly. However, in the actual working condition where the end position of the branch pipe 3 changes from circular array distribution to determinant distribution, at least a part of the ends of multiple closely arranged branch pipes 3 need to be bent and adjusted. During the adjustment, double spatial interference will occur: the branch pipes 3 on the middle circular ring have insufficient bending space due to the double position restrictions of the inner and outer ring branch pipes, and it is difficult for their ends to be inserted into the transfer positioning hole 201 with a diameter basically equal to theirs after bending. For the outer ring branch pipes 3, since the transfer positioning hole 201 deviates far from the original circular distribution axis, a large bending amplitude is required to achieve assembly; such a large bending not only poses a challenge to the mechanical properties of the branch pipe material, but also the change in the curvature of the inner flow channel of the branch pipe will increase the refrigerant flow resistance and affect the distribution uniformity. In addition, when multiple rings of branch pipes 3 are synchronously assembled into the equal-diameter transfer positioning holes 201, the accumulation of geometric tolerances will also exacerbate the assembly difficulty.

[0078] Therefore, as Figure 5 (To visually represent the assembly relationship between the branch pipe 3 and the transfer positioning hole 201, Figure 5 only four branch pipes at the cross-sectioned areas are retained in Figure 6 ), as shown in

[0079] In this embodiment, which is provided on the branch pipe adapter plate 20, the aperture of at least a part of the transfer positioning holes 201 is larger than the outer diameter of the branch pipe 3 to be assembled with it. The adjustment gap 2011 between the transfer positioning hole 201 and the branch pipe 3 is used to form a bending compensation space. When the branch pipe 3 is bent under restriction, it can adaptively adjust the spatial position of its end by means of the adjustment gap 2011 so that it can be quickly assembled into the corresponding transfer positioning hole 201. This design converts the traditional rigid assembly with completely matching pipe diameters into an elastic assembly based on the adjustment gap 2011, reduces the bending accuracy requirements when the spatial position of the end of the branch pipe 3 is converted, and resolves the influence of spatial interference on the conversion of multiple branch pipes 3 from circular array distribution to determinant distribution.

[0079] In this embodiment, the end diameters of multiple branch pipes 3 are the same, and the aperture diameter of each adapter positioning hole 201 is larger than the outer diameter of the corresponding branch pipe 3. However, the present invention does not make any limitation thereto. In other embodiments, for an adapter positioning hole whose center position deviates not far from the center of the corresponding branch pipe end before bending, the aperture diameter thereof may also be set to be substantially close to the outer diameter of the corresponding branch pipe; for an adapter positioning hole with a relatively large deviation, the aperture diameter thereof is still set to be larger than the outer diameter of the corresponding branch pipe; that is, the aperture diameters of multiple adapter positioning holes are not equal, some aperture diameters are close to the outer diameters of the corresponding branch pipes, while some other aperture diameters are larger than the outer diameters of the corresponding branch pipes. For the deviation distance between the center of the adapter positioning hole and the center of the corresponding branch pipe end before bending, specifically, the row projection distance and column projection distance of the center of the adapter positioning hole and the center of the corresponding branch pipe end before bending on the branch pipe adapter plate can be calculated. When at least one of the two exceeds the set distance, the aperture diameter of this adapter positioning hole can be set to be larger than the outer diameter of the corresponding branch pipe. However, the present invention does not make any limitation thereto.

[0080] Specifically, in this embodiment, the aperture diameters of each adapter positioning hole 201 are equal and larger than the outer diameter of the corresponding branch pipe 3. However, the present invention does not make any limitation thereto. In other embodiments, the aperture diameter of each adapter positioning hole can also be set to be larger than the outer diameter of the corresponding branch pipe, but the aperture diameters between each adapter positioning hole may not be equal.

[0081] When the refrigerant distribution assembly provided in this embodiment is assembled in a shell-and-tube heat exchanger, the sealed connection between multiple branch pipes 3 and the corresponding heat exchange pipes is realized through the structural cooperation between the branch pipe adapter plate 20 and the tube sheet. Specifically, as Figure 12 and Figure 13 shown, the branch pipe adapter plate 20 is arranged inside the tube box, and its outer periphery is hermetically welded to the tube sheet 230 to form a sealed cavity 240 therebetween. The ends of each branch pipe 3 are inserted into the heat exchange pipes 210 fixed on the tube sheet 230 in the sealed cavity 240. This design uses the unified indirect sealing of the sealed cavity 240 to replace the individual sealing of single pipes. The connection between the branch pipe 3 and the heat exchange pipe 210 does not require separate sealing treatment, but relies on the overall sealing performance of the sealed cavity 240 to prevent the leakage of the tube-side medium, significantly reducing the assembly complexity of the multi-branch pipe system and realizing the synchronous and precise docking of multiple pipes.

[0082] To ensure the sealing reliability, the peripheral wall of each branch pipe 3 needs to be hermetically welded in the corresponding adapter positioning hole 201 in this structure. In this embodiment, since the aperture diameter of each adapter positioning hole 201 is larger than the outer diameter of the corresponding branch pipe 3, to realize the sealed welding between the two, as Figure 4As shown in the figure, the branch pipe adapter plate 20 of this embodiment further includes an adjustment bushing 202 sleeved on the outer peripheral wall of the branch pipe 3 and inserted into the transfer positioning hole 201. The branch pipe 3 is hermetically welded to the corresponding transfer positioning hole 201 through the adjustment bushing 202. However, the present invention does not make any limitations in this regard. In other embodiments, when the aperture of the transfer positioning hole is substantially close to the outer diameter of the corresponding branch pipe, the outer peripheral wall of the branch pipe can be directly hermetically welded to the transfer positioning hole without setting an adjustment bushing, such as using brazing or self-fusion welding with the melting of the base material.

[0083] In this embodiment, on the side of the branch pipe adapter plate 20 close to the distribution body 1, at least a part of the branch pipes 3 are formed with bending portions 31 so that their ends are converted from a circular array distribution to a determinant distribution. The bending of the branch pipe 3 will change the direction of its internal flow path. When the refrigerant output from the distribution hole 12 reaches the bending portion 31, blocked by the inner wall of the outer side of the bending portion 31 (the inner wall farthest from the bending center in the radial direction), part of the refrigerant will be reflected back upstream. The pressure wave generated by the reflection will continue to propagate upstream, and the pressure wave whose acting direction is opposite to the refrigerant flow direction will hinder the refrigerant from entering the distribution hole 12, affecting the refrigerant distribution amount in this branch pipe 3 and causing uneven distribution problems. Further, the influence of the reflected pressure wave increases with the increase of the bending angle θ. The bending angle θ refers to the included angle between the extension line of the central axis of the upstream end of the bending portion 31 and the extension line of the central axis of the downstream end of the bending portion 31, as Figure 5 shown.

[0084] To reduce the influence of the bending portion 31 on the refrigerant distribution uniformity, in this embodiment, it is set that when the bending angle θ is greater than or equal to 10 degrees, the length L of the straight pipe section 32 between the upstream end of the bending portion 31 and the inner end of the branch pipe 3 inserted into the distribution hole 12 is L≥8mm, as Figure 5 shown. In this embodiment, by setting the length L of the straight pipe section 32, an attenuation distance is provided for the reflected pressure wave to ensure that the pressure wave is completely attenuated before reaching the distribution hole 12, thereby well solving the influence of the downstream pressure wave reflection generated by the bending portion on the refrigerant distribution uniformity at the distribution hole 12. Preferably, the length L of the straight pipe section 32 can be set to 10mm, 15mm, 18mm or a value of 20 mm or more.

[0085] When the branch pipe 3 is bent, to accurately control the required length L of the straight pipe section 32, this embodiment sets that the distributor 10 further includes a straight pipe sleeve 4 sleeved on the straight pipe section 32 and inserted into the distribution hole 12. The bending portion 31 on the branch pipe 3 is located at the downstream end of the straight pipe sleeve 4, and the length of the straight pipe section 32 is accurately controlled based on the straight pipe sleeve 4 when the bending portion 31 is formed, as Figure 5 shown. In addition, when bending, the setting of the straight pipe sleeve 4 can also protect the root of the branch pipe 3 (i.e., the connection part of the branch pipe 3 and the distribution body 1) to avoid the root of the branch pipe 3 from breaking due to excessive bending angle and improve the reliability of the bending process.

[0086] In this embodiment, the branch pipe 3 is an integral pipe fitting with substantially the same inner diameter. However, the present invention does not make any limitation thereto. In other embodiments, the branch pipe may also include a connecting pipe section and a branch pipe extension section, and the inner diameter of the connecting pipe section is greater than or equal to the inner diameter of the branch pipe extension section.

[0087] The setting of the branch pipe adapter plate 20 not only converts the ends of multiple circles of branch pipes 3 distributed in a circular array on the distributor 10 into a row-column distribution, but also provides modular sealing for multiple branch pipes 3 and corresponding heat exchange pipes 210 through the sealing cavity 240, taking into account the process adaptability under different tolerance fits while ensuring airtightness. Regarding the refrigerant distribution uniformity and the layout of multiple branch pipes 3, in this embodiment, the internal flow path in the distribution body 1 is precisely designed by improving the structures of the distribution body 1 and the liquid equalizing partition plate 2. While expanding the number of branch pipes 3 based on the determined size of the distribution body 1, the two-phase flow refrigerant is evenly distributed into the expanded multiple branch pipes 3.

[0088] In this embodiment, as Figure 2 and Figure 2A shown, the distribution body 1 includes a cylindrical tube body 1A, an end cover 1B, and a lining plate 1C, and the three jointly enclose a receiving cavity 13. The end cover 1B is hermetically welded to the liquid inlet end of the cylindrical tube body 1A, and a liquid inlet hole 11 is formed thereon. The lining plate 1C is embedded and hermetically welded to the liquid outlet end of the cylindrical tube body 1A, and multiple circles of distribution holes 12 are formed on the lining plate 1C by stamping. However, the present invention does not make any limitation thereto. In other embodiments, the distribution body 1' may also be provided to include a cylindrical barrel body 1A' with a single open end and an end cover 1B. The end cover 1B is hermetically welded to the open end of the cylindrical barrel body 1A', and a liquid inlet hole 11 is formed. Multiple circles of barrel through holes are formed by stamping at the bottom of the cylindrical barrel body 1A' to form multiple circles of distribution holes 12. Specifically, in Figure 10 it, the distribution body 1 further includes a lining plate 1C provided on the inner bottom wall of the cylindrical barrel body 1A'. Lining plate through holes corresponding to the multiple circles of barrel through holes are formed on the lining plate 1C, and the lining plate through holes and the corresponding barrel through holes jointly form the distribution holes 12. Or, in other embodiments, the distribution body is provided to include an end cover and a lining plate. A liquid inlet hole is formed on the end cover, and a cylindrical straight section is formed at the open end of the end cover. The lining plate is embedded and hermetically welded to the cylindrical straight section to enclose a receiving cavity.

[0089] In this embodiment, as Figure 8 and Figure 9 shown, the liquid equalizing partition plate 2 uses concentric multiple circles of circular arrays for the design of the partition holes 21 to achieve precise distribution. For multiple partition holes 21 distributed in the same circle, an equal center distance layout is adopted to ensure that the flow path lengths of the respective partition holes 21 are substantially the same, thereby achieving uniform distribution in this circle. In terms of across circles, it is defined that the center distance between adjacent partition holes 21 on the i-th circle is L i, the center distance between adjacent partition holes 21 on the j-th circle is L j , by restricting the difference in the center distances of the partition holes between any two circles

[0090] △L 12 =∣L1 - L2∣≤1.2 mm, ensuring similar refrigerant flow characteristics between different circles, thereby realizing the control of the flow distribution uniformity of the multi-circle partition holes 21. In this embodiment, two circles of partition holes 21 are formed on the liquid distribution partition 2. The center distance between adjacent two partition holes 21 on the inner circle is L1, and the center distance between adjacent two partition holes 21 on the outer circle is L2. The center distance difference △L 12 =∣L1 - L2∣≤1.2 mm. Preferably, the center distance difference △L between any two circles of partition holes can be set ij to 0.2 mm, 0.5 mm, 0.8 mm, 1 mm or other values less than or equal to 1.2 mm.

[0091] Although this embodiment is described by taking the liquid distribution partition 2 having two circles of partition holes 21 as an example. However, the present invention does not make any limitation thereto. In other embodiments, multiple circles of partition holes can also be provided on the liquid distribution partition, such as partition holes with more than three circles. Taking three circles of partition holes as an example, at this time, the center distance difference between the first circle and the second circle of partition holes is △L 12 , the center distance difference between the first circle and the third circle of partition holes is △L 13 , the center distance difference between the second circle and the third circle of partition holes is △L 23 ; △L 12 , △L 13 and △L 23 are all less than or equal to 1.2 mm, and as for whether the center distance differences among the three are equal, the present invention does not make any limitation thereto.

[0092] In this embodiment, as Figure 8 and Figure 9 shown, the liquid distribution partition 2 is a plate structure with both sides approaching a planar shape, and the projection area 22 of the liquid inlet hole 11 on the liquid distribution partition 2 is also a planar structure. The multi-circle partition holes 21 are located on the plane of the liquid distribution partition 2 outside the projection area 22. However, the present invention does not make any limitation thereto.

[0093] In this embodiment, the partition hole 21 is a flanging hole with an inner wall busbar in an arc shape and a hole diameter that gradually decreases along the flow direction of the refrigerant. The gradual reduction of the inner diameter of the partition hole 21 can accelerate the refrigerant flowing through, increase the refrigerant flow rate so that it can quickly enter the corresponding distribution hole 12; in addition, the acceleration of the partition hole 21 can also further promote the mixing of the gas-liquid two-phase refrigerant. However, the present invention does not make any limitation in this regard. In other embodiments, the partition hole can be set as an arc bubble hole with the hole wall convex in an arc shape to one side or both sides of the liquid equalizing partition. Or, the partition hole can be set as a converging hole with an inner wall busbar in an inclined straight line and a hole diameter that gradually decreases along the flow direction of the refrigerant. Or, the partition hole can be set as a through hole with a substantially uniform hole diameter along the flow direction of the refrigerant (such as Figure 10 and Figure 11 shown), and the shape of the through hole is any one or a combination of a circle, an ellipse or a waist shape.

[0094] In this embodiment, as Figure 2 shown, the distributor 1 further 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 substantially constant inner diameter and a jet section 52 located downstream of the main body section 51 and with an inner diameter reduced relative to the main body section 51. The jet section 52 increases the speed of 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 hits the projection area 22 of the liquid inlet hole 11 on the liquid equalizing partition 2 to enhance the reflection effect. In Figure 2 , the jet section 52 is a straight section with an inner diameter reduced relative to the main body section 51. However, the present invention does not make any limitation in this regard. In other embodiments, the jet section 52 can also be a Venturi tube section with a jet throat, such as Figure 10 shown.

[0095] Correspondingly, as Figure 12 shown, this embodiment also provides a shell-and-tube heat exchanger, which includes a heat exchanger shell (its structure is the same as that of the existing shell-and-tube heat exchanger, so the figure is not shown) and a tube-side assembly 200 arranged in the heat exchanger shell. The tube-side assembly 200 includes a plurality of heat exchange tubes 210 and the refrigerant distribution assembly 220 for the shell-and-tube heat exchanger described above. A plurality of branch pipes 3 in the refrigerant distribution assembly 220 for the shell-and-tube heat exchanger are hermetically connected to the plurality of heat exchange tubes 210 through a branch pipe adapter plate 20 respectively.

[0096] Specifically, as Figure 12 and Figure 13As shown, the tube side assembly 200 further includes a tube sheet 230, and a plurality of heat exchange tubes 210 are sequentially assembled into a plurality of tube sheet assembly holes (not shown as they are for heat exchange tube assembly) distributed in rows and columns on the tube sheet 230. A tube box (with the same structure as that of the existing shell and tube heat exchanger, so not shown in the figure) is formed between the tube sheet 230 and the end cover of the heat exchanger shell. The branch pipe adapter plate 20 is arranged in the tube box, and its outer periphery is hermetically welded to the tube sheet 230 to form a sealing cavity 240 therebetween. The peripheral wall of each branch pipe 3 is hermetically welded to the adapter positioning hole 201, and the end of each branch pipe 3 is inserted into the corresponding heat exchange tube 210 at the sealing cavity 240. To more intuitively observe the connection between each branch pipe 3 and the corresponding heat exchange tube 210, Figure 12 only the connection between some of the branch pipes 3 and the corresponding heat exchange tubes 210 is shown. In an actual shell and tube heat exchanger, the number of branch pipes 3 and heat exchange tubes 210 will be more.

[0097] In this embodiment, the sealing cavity 240 formed by the branch pipe adapter plate 20 and the tube sheet 230 is used to integrally and uniformly seal the joints of all the branch pipes 3 and the heat exchange tubes 210. Specifically, this sealing method no longer requires separate plugging of the connection nodes between each branch pipe 3 and the heat exchange tube 210, effectively eliminating the need for point-by-point sealing operations common in multi-pipeline systems. It can not only reduce the number of sealing points to improve sealing reliability, but also greatly reduce the assembly progress requirements between the branch pipes 3 and the corresponding heat exchange tubes 210, which is more conducive to the overall assembly of multiple branch pipes 3.

[0098] In this embodiment, the heat exchange tubes 210 are U-shaped tube bundles, and the tube side assembly 200 includes two refrigerant distribution assemblies 220 for shell and tube heat exchangers ( Figure 12 the cross-sectional view only shows one refrigerant distribution assembly 220 for shell and tube heat exchangers) arranged on the end covers on the same side of the heat exchanger shell. The distributor 10 in each refrigerant distribution assembly 220 for shell and tube heat exchangers evenly distributes the refrigerant to the input ports of the plurality of U-shaped heat exchange tubes 210 corresponding to its distribution, and the output ports of the U-shaped heat exchange tubes 210 are connected to the collector on the heat exchanger shell to output the evaporated gaseous refrigerant from the shell and tube heat exchanger. However, the present invention makes no limitation in this regard. In other embodiments, one or more than three refrigerant distribution assemblies for shell and tube heat exchangers can also be provided.

[0099] In addition, in other embodiments, such as Figure 14AAs shown, when the heat exchange tubes 210 are straight tube bundles, the tube-side assembly 200 includes a refrigerant distribution assembly 220 for a shell-and-tube heat exchanger disposed on one end cover of the heat exchanger housing and another refrigerant distribution assembly 220' for a shell-and-tube heat exchanger disposed on the other end cover of the heat exchanger housing. The distributor 10 in the refrigerant distribution assembly 220 for a shell-and-tube heat exchanger evenly distributes the refrigerant to the input ports of a group of multiple straight tube heat exchange tubes 210 corresponding to it. The output ports of the multiple straight tube heat exchange tubes 210 are collected by a collector or a collection chamber 100 located inside the other end of the heat exchanger housing; the collected refrigerant enters another refrigerant distribution assembly 220' connected to another tube sheet 230', and is distributed to the input ports of another group of multiple straight tube heat exchange tubes 210' corresponding to it through multiple branch pipes 3'. The evaporated gaseous refrigerant is output from the output ports of the other multiple straight tube heat exchange tubes 210' outside the shell-and-tube heat exchanger.

[0100] Figure 14B A shell-and-tube heat exchanger with straight tube bundles provided by another embodiment of the present invention. In this structure, the refrigerant distribution assembly 220 for a shell-and-tube heat exchanger is only assembled at one end of the heat exchanger housing, and the other end of the heat exchanger housing is collected through the collection chamber 100' and then redistributed into another group of multiple straight tube heat exchange tubes 210'.

[0101] In the refrigerant distribution assembly 220 for a shell-and-tube heat exchanger provided in this embodiment, the distribution body 1, the liquid equalizing partition 2 and multiple circles of partition holes 21 on it are arranged so that the distributor 10 can fully mix the two-phase refrigerant into a dispersed flow pattern that can weaken the influence of gravity to achieve uniform distribution. This makes the distributor 10 provided in this embodiment not affected by the installation angle, and it can be arranged in the heat exchanger housing along a direction basically parallel to the axial direction of the heat exchanger housing, such as Figure 12 、 Figure 14A and Figure 14B shown; it can also be arranged in the heat exchanger housing along a direction basically perpendicular to the axial direction of the heat exchanger housing; at this time, each branch pipe 3 is bent so that its end is inserted into the transfer positioning hole 201 on the branch pipe transfer plate, such as Figure 14C .

[0102] In the shell-and-tube heat exchanger provided in this embodiment, the outer peripheral wall of the distribution body 1 can be hermetically fixed to the end cover of the heat exchanger housing and extend along a direction basically parallel to the axial direction of the heat exchanger housing. Multiple branch pipes 3 and the branch pipe transfer plate 20 all extend into the tube box to connect the tube sheet 230. However, the present invention does not make any limitation in this regard. In other embodiments, when the distribution body is arranged in the heat exchanger housing along a direction basically perpendicular to the axial direction of the heat exchanger housing, the distribution body can be fixed to the inner wall of the heat exchanger housing.

[0103] Correspondingly, this embodiment also provides a refrigeration device, which includes the above-mentioned shell-and-tube heat exchanger.

[0104] Example Two

[0105] This embodiment is basically the same as Example One and its variations, except that: the assembly method between the branch pipe 3 and the branch pipe adapter plate 20 is different, and the sealing method between the branch pipe 3 and the corresponding heat exchange pipe 210 is different.

[0106] As Figure 15 and Figure 16 shown, in this embodiment, each branch pipe 3 is only limited to be located within the transfer positioning hole 201 without being sealed and welded to the transfer positioning hole 201. In this structure, the transfer positioning hole 201 limits the end position of each branch pipe 3 to facilitate its rapid assembly into multiple heat exchange pipes 210 within the shell-and-tube heat exchanger. For the transfer positioning hole 201, similar to Example One, at least a part of the aperture of the transfer positioning hole 201 can be set to be larger than the outer diameter of the branch pipe 3 assembled therewith, so that when multiple circles of branch pipes 3 are bent under restriction, they can adaptively adjust the spatial position of their ends by means of the adjustment gap 2011, and then be quickly assembled into the corresponding transfer positioning holes 201.

[0107] Correspondingly, as Figure 17 shown, in the shell-and-tube heat exchanger provided in this embodiment, the end of each branch pipe 3 extends out of the transfer positioning hole 201 to be welded to the corresponding heat exchange pipe 210 within the shell-and-tube heat exchanger. Compared with Example One, although each branch pipe 3 in this embodiment needs to be sealed and welded to the corresponding heat exchange pipe 210, this structure can cancel the tube sheet within the shell-and-tube heat exchanger. Canceling the tube sheet can, on the one hand, simplify the structure of the shell-and-tube heat exchanger to reduce its component costs and installation procedures; on the other hand, after canceling the tube sheet, the exchange area between the refrigerant and the shell-side medium can be extended, and even the refrigerant transmitted within the branch pipe 3 can conduct heat exchange with the shell-side medium through the wall of the branch pipe 3, reducing the heat loss during the refrigerant distribution process and improving the heat exchange efficiency.

[0108] In this embodiment, a brazing layer 250 for sealed connection is formed between the branch pipe 3 and the corresponding heat exchange pipe 210 by brazing. Specifically, flame brazing can be used. However, the present invention makes no limitation thereto.

[0109] Although this embodiment Figure 17 uses the heat exchange pipe 210 of the U-shaped tube bundle as an example for illustration. However, the present invention makes no limitation thereto. In other embodiments, the connection structure between the branch pipe and the heat exchange pipe provided in this embodiment can also be applied to a straight-tube shell-and-tube heat exchanger.

[0110] For the specific structures of the distributor and other components within the heat exchanger shell, this embodiment is basically the same as Example One and its variations, and will not be elaborated herein.

[0111] Example Three

[0112] This embodiment is basically the same as Embodiment 1 and its variations, except that: as Figure 19 shown, the dispenser 10 further includes a flow guiding member 6 disposed within the dispensing chamber 130 and on the inner circumference of the multi-turn dispensing holes 12. An annular flow passage communicating with the multi-turn dispensing holes 12 is defined between the flow guiding member 6 and the peripheral wall of the dispensing body 1.

[0113] In this embodiment, by providing the flow guiding member 6, the volume of the dispensing chamber 130 is reduced to maintain the refrigerant flow rate ejected from the multi-turn partition holes 21, ensuring that the refrigerant has sufficient inertial force within the dispensing chamber 130 to overcome the influence of gravity and preventing the refrigerant after mixing from undergoing gas-liquid two-phase segregation again. At the same time, the annular flow passage defined between the flow guiding member 6 and the inner wall of the dispensing chamber 130 can also uniformly guide the fully mixed homogeneous refrigerant into the multi-turn dispensing holes 12.

[0114] In the shell-and-tube heat exchanger provided in this embodiment, although the flow guiding member 6 is provided within the dispenser 10, the flow guiding member 6 is located on the inner circumference of the multi-turn dispensing holes 12 and does not affect the processing and arrangement of the multi-turn dispensing holes 12 on the dispensing body 1. At the same time, the multi-turn dispensing holes 12 can still be in one-to-one correspondence with the multi-turn partition holes 21 on the liquid distribution partition 2 through the cylindrical dispensing chamber 130, thereby realizing the expansion of the number of branch pipes 3. Further, in this embodiment, the flow guiding member 6 is welded in a split manner to the inner wall of the lining plate 1C on the liquid outlet side of the dispensing body 1. This setting can further reduce the influence of the flow guiding member 6 on the processing of the multi-turn dispensing holes 12. However, the present invention does not make any limitation in this regard. In other embodiments, the flow guiding member can also be integrally formed with a baffle located inside the lining plate, and a multi-turn baffle hole coaxial with the multi-turn dispensing holes is formed on the baffle, but the aperture of the baffle hole is smaller than the outer diameter of the insertion end of the branch pipe to achieve the insertion limit of the branch pipe.

[0115] In this embodiment, as Figure 19 shown, the flow guiding member 6 is a cylindrical spacer sleeve. One end of the spacer sleeve abuts against the area of the liquid distribution partition 2 on the inner circumference of the multi-turn partition holes 21, and the other end thereof abuts against the liquid outlet end of the dispensing body 1 on the inner circumference of the multi-turn dispensing holes 12. Preferably, in this structure, the radial distance L1' from the outer peripheral wall of the spacer sleeve (i.e., the flow guiding member 6) to the inner edge of the innermost turn of the dispensing holes 12 satisfies: L1' ≤ 4 mm. Here, the inner edge of the innermost turn of the dispensing holes refers to the intersection point K of the connection line between the center of the innermost turn of the dispensing holes 12 and the center of the liquid outlet end of the dispensing body 1 and the edge of the innermost turn of the dispensing holes 12 on the liquid outlet end of the dispensing body 1.

[0116] However, the present invention does not make any limitation in this regard. In other embodiments, the flow guiding member 6 can also be set as a flow guiding cone. The bottom of the flow guiding cone is disposed at the liquid outlet end of the dispensing body 1 on the inner circumference of the multi-turn dispensing holes 12, and its end extends towards the liquid distribution partition 2, as Figure 20 shown.

[0117] For the specific structures of the liquid inlet pipe, the distribution body, the branch pipe adapter plate, and other components inside the heat exchanger housing, this embodiment is basically the same as Embodiment 1 and its variations, and will not be elaborated here.

[0118] Embodiment 4

[0119] This embodiment is basically the same as Embodiment 1 and its variations, except that: the structure of the liquid equalizing partition plate 2 is different.

[0120] In this embodiment, as Figure 21 shown, the projection area 22 on the liquid equalizing partition plate 2 opposite to the liquid inlet hole 11 bulges into the distribution cavity 130 to form a mixing concave cavity 23 with an opening facing the liquid inlet hole 11. The mixing concave cavity 23 provides a mixing space for the refrigerant during the maximum kinetic energy stage after the refrigerant is reflected, enhancing the degree of disorder to promote the gas-liquid two-phase mixing. At the same time, when the mass flow rate and flow velocity of the input refrigerant are relatively large, the setting of the mixing concave cavity 23 can also effectively reduce the influence of the reflection force on the input refrigerant, avoiding the refrigerant flowing back to the liquid inlet hole 11 due to excessive reflection force.

[0121] As Figure 21 , Figure 22 and Figure 23 shown, the mixing concave cavity 23 is a cylindrical cavity with a square cross-sectional contour line, and the outer bottom surface of the mixing concave cavity 23 abuts against the inner bottom wall of the liquid outlet end of the distribution body 1. At this time, preferably, the radial distance L1 from the outer peripheral wall of the mixing concave cavity 23 to the inner edge of the innermost distribution hole satisfies: L1 ≤ 4 mm. The inner edge of the innermost distribution hole refers to: at the liquid outlet end of the distribution body 1, the intersection K of the line connecting the center of the innermost distribution hole 12 and the center of the liquid outlet end of the distribution body 1 and the edge of the innermost distribution hole 12. However, the present invention does not make any limitation in this regard.

[0122] Although this embodiment is described by taking the mixing concave cavity 23 abutting against the inner wall of the liquid outlet end of the distribution body 1 as an example. However, the present invention does not make any limitation in this regard. In other embodiments, it is also possible to set the outer bottom surface of the mixing concave cavity not to abut against the inner bottom wall of the liquid outlet end of the distribution body. For the shape of the mixing concave cavity, in other embodiments, it is also possible to set the mixing concave cavity as a prism with a square cross-sectional contour line, a frustum of a cone or a prism with a trapezoidal cross-sectional contour line (as Figure 24 shown), a cone or a pyramid with a triangular cross-sectional contour line (as Figure 25 shown), and one or more combinations of a partial circle in the cross-sectional contour line; such as a combination of a cylinder and a partial sphere (as Figure 26 shown), a combination of a frustum of a cone and a partial sphere, a combination of a prism and a partial sphere, etc.

[0123] Although this embodiment is described by taking the projection area 22 of the projection area protruding into the distribution cavity 130 to form a mixing cavity 23 with an opening facing the liquid inlet hole 11 as an example. However, the present invention does not make any limitations thereto. In other embodiments, the projection area of the liquid inlet hole on the partition plate may also protrude toward the side where the liquid inlet hole is located, and the protruding part may be a spherical bubble with a partial circular longitudinal section contour line, a pyramid with a square longitudinal section contour line, a frustum of a cone or a frustum of a pyramid with a trapezoidal longitudinal section contour line, a cone or a frustum of a cone with a triangular longitudinal section contour line, or a combination of one or more of them.

[0124] Similar to the plate-type liquid distribution partition plate with both side surfaces being close to a plane in the first embodiment, the liquid distribution partition plate structure provided in this embodiment can also be matched with the flow guiding member in the third embodiment, such as Figure 27 As shown, a spacer sleeve serving as a flow guiding member 6 is additionally provided outside the mixing cavity 23. In addition, in other embodiments, when the projection area of the liquid inlet hole on the liquid distribution partition plate protrudes toward one side of the liquid distribution partition plate, a spacer sleeve or a flow guiding cone serving as a flow guiding member may also be provided in the distribution cavity.

[0125] Similarly, for the specific structures of the liquid inlet pipe, the distribution body, the branch pipe adapter plate, and other components in the heat exchanger housing, this embodiment is basically the same as the first embodiment and its variations, and will not be elaborated here.

[0126] Embodiment Five

[0127] This embodiment is basically the same as the first embodiment and its variations, and the difference is that: as Figure 28 As shown, in this embodiment, the distributor 10 further includes a jet member 7 disposed in the distribution cavity 130, and a jet hole 71 is formed on the jet member 7 and the jet hole 71 is opposite to the projection area 22 of the liquid inlet hole 11 on the liquid distribution partition plate 2.

[0128] In this embodiment, by adding the jet member 7 to accelerate the flow rate of the refrigerant after the flow pattern is sorted by the liquid distribution partition plate 2, a secondary jet is formed (the primary jet is the acceleration of the refrigerant at the jet section 52 on the liquid inlet pipe 5), so that the refrigerant can always maintain a uniformly mixed dispersed flow pattern during the process of redistribution after setting, thereby improving the distribution uniformity.

[0129] In this embodiment, the distributor 10 further includes a reflection mixing and flow guiding plate 8 disposed in the distribution cavity 130 and downstream of the jet member 7. The reflection mixing and flow guiding plate 8 has multiple circles of flow guiding holes 81 corresponding to the plurality of distribution holes 12 one by one and distributed in an annular array. The multiple circles of flow guiding holes 81 are distributed on the outer peripheral plane of the projection area of the jet hole 71 on the reflection mixing and flow guiding plate 8.

[0130] In this embodiment, the projection area of the jet holes 71 on the reflection mixing deflector 8 protrudes and extends towards the liquid outlet side of the distribution body 1 to form a reflection mixing cavity 82 with an opening facing the jet holes 71. The bottom wall of the reflection mixing cavity 82 reflects the refrigerant ejected from the jet holes 71, and the reflected refrigerant collides violently in the reflection mixing cavity 82, further enhancing the degree of two-phase flow disorder to promote the full mixing of the refrigerant. In this embodiment, the reflection mixing cavity 82 is a cylindrical cavity with a square cross-sectional contour line. However, the present invention does not make any limitation in this regard. In other embodiments, the shape of the mixing cavity may also be a prism with a square cross-sectional contour line, a frustum of a cone or a prism with a trapezoidal cross-sectional contour line, a cone or a pyramid with a triangular cross-sectional contour line, and one or more combinations of a partially circular cross-sectional contour line; such as a combination of a cylinder and a partial sphere, a combination of a frustum of a cone and a partial sphere, a combination of a prism and a partial sphere, etc.

[0131] Although this embodiment takes the formation of the reflection mixing cavity 82 on the reflection mixing plate 8 as an example. However, the present invention does not make any limitation in this regard. In other implementations, the downstream surface of the reflection mixing deflector 8 may also be set to be close to a plane, and the distributor 10 further includes a deflector 6 disposed in the flow splitting cavity 130 and downstream of the reflection mixing deflector 8. The deflector 6 is located inside the circumference of the multi-loop distribution holes 12, and an annular flow channel communicating with the multi-loop distribution holes 12 is formed between the deflector 6 and the peripheral wall of the distribution body 1. Specifically, the deflector 6 may be a cylindrical spacer sleeve. One end of the spacer sleeve abuts against the area of the reflection mixing deflector 8 inside the circumference of the multi-loop deflector holes 81, and the other end thereof abuts against the liquid outlet end of the distribution body 1 inside the circumference of the multi-loop distribution holes 12, as Figure 29 shown. Or, the deflector 6 is a deflector cone, the bottom of the deflector cone 6 is disposed at the liquid outlet end of the distribution body 1 inside the circumference of the multi-loop distribution holes 12, and its end extends towards the reflection mixing deflector 8, as Figure 30 shown.

[0132] In addition, in other embodiments, a reflection mixing deflector may not be provided downstream of the jet member 7, and only a deflector cone (i.e., the deflector 6) may be provided, as Figure 31 shown.

[0133] Although Figures 28 to 31 in, the liquid equalizing partition plate 2 is a plate structure with both side surfaces being flat. However, the present invention does not make any limitation in this regard. In other embodiments, the projection area 22 of the liquid inlet hole 11 on the liquid equalizing partition plate 2 may also protrude towards one side of the liquid equalizing partition plate 2 to form a mixing cavity 23, as Figure 32 shown.

[0134] Similarly, for the specific structures of the liquid inlet pipe, the distribution body, the branch pipe adapter plate, and other components inside the heat exchanger housing, this embodiment is basically the same as that of the first embodiment and its variations, and will not be elaborated here.

[0135] Embodiment Six

[0136] This embodiment is basically the same as Embodiment 5 and its variations, except that: in this embodiment, the projection area 22 of the liquid inlet hole 11 on the liquid distribution partition 2 bulges towards the side where the jet member 7 is located to form a mixing concave cavity 23. The setting of the mixing concave cavity 23 on the liquid distribution partition 2 enables the refrigerant after reflection to participate in mixing with the maximum kinetic energy, thereby increasing the degree of disorder of the two-phase flow. However, limited by the depth of the mixing concave cavity 23 and the inner diameter of the distribution body 1, the volume of the flow pattern maintaining cavity 102 surrounded by the liquid distribution partition 2 and the jet member 7 may be relatively large. The initially dispersed flow pattern formed after being sorted by the pre-rectifying cavity 101 surrounded by the liquid distribution partition 2 and the liquid inlet end of the distribution body 1 is very likely to experience gas-liquid separation again due to excessive expansion after entering the overly large flow pattern maintaining cavity 102.

[0137] To solve this problem, as Figure 33 and Figure 34 shown, the distributor 10 further includes a partition plate 9 disposed between the liquid distribution partition 2 and the jet member 7. The partition plate 9 divides the flow pattern maintaining cavity 102 surrounded by the liquid distribution partition 2 and the jet member 7 into a first maintaining cavity 1021 and a second maintaining cavity 1022. A plurality of partition plate through holes 91 communicating the first maintaining cavity 1021 and the second maintaining cavity 1022 are formed on the partition plate 9. Among them, the volume V1 of the pre-rectifying cavity 101, the volume V21 of the first maintaining cavity 1021, and the volume V22 of the second maintaining cavity 1022 satisfy: 0.75 ≤ V1 / V21 ≤ 1.3, 0.75 ≤ V21 / V22 ≤ 1.3. The setting of the partition plate 9 precisely controls the degree of expansion of the refrigerant when flowing between adjacent chambers, ensuring that the refrigerant can develop into a stable dispersed flow pattern after flowing through the first maintaining cavity 1021 and the second maintaining cavity 1022.

[0138] In this embodiment, as Figure 33 and Figure 34 shown, an avoidance hole 92 is formed on the partition plate 9 opposite to the mixing concave cavity 23, and the partition plate 9 is sleeved on the outer periphery of the mixing concave cavity 23 through the avoidance hole 92. At this time, the pre-rectifying cavity 101 refers to the chamber surrounded by the plane of the upstream surface of the liquid distribution partition 2 at the partition hole 21 and the inner wall of the body liquid inlet end 11, as Figure 33 the area shown by the dotted line in Figure 33 The first maintaining cavity 1021 is an annular chamber surrounding the mixing concave cavity 23 surrounded by the downstream surface of the liquid distribution partition 2 and the upstream surface of the partition plate 9, as Figure 33 the area shown by the center dotted line in

[0139] In this embodiment, the multiple partition plate through-holes 91 on the partition plate 9 and the multiple circles of partition holes 21 on the liquid equalizing partition plate 2 are misaligned. This setting enables the refrigerant preliminarily rectified in the pre-rectifying cavity 101 not to directly flow through to the second maintaining cavity 1022, but to enter the second maintaining cavity 1022 for further mixing and development after being mixed and developed in the first maintaining cavity 1021 and then passing through the multiple partition plate through-holes 91.

[0140] Similar to Embodiment Five, in this embodiment, the distributor 10 may further include a reflection mixing and guiding plate 8 and a guiding member 6 (as Figure 35 shown) located downstream of the jet member 7. However, the present invention makes no limitation thereto. In other embodiments, a reflection mixing and guiding plate may also be provided downstream of the jet member, or only a guiding cone serving as a guiding member may be provided, or no components may be provided at all.

[0141] Similarly, for the specific structures of the liquid inlet pipe, the distribution body, the branch pipe adapter plate, and other components within the heat exchanger housing, this embodiment is basically the same as Embodiment One and its variations, and will not be elaborated herein.

[0142] In summary, the refrigerant distribution assembly for the shell-and-tube heat exchanger provided by the present invention divides the accommodation cavity within the distribution body into two or more chambers through the liquid equalizing partition plate, while providing a space for refrigerant mixing and distribution, suppressing the problem of excessive refrigerant expansion caused by an overly large cavity. The distribution body adopts a hollow columnar design, and the inner cavity cross-section thereof and the multiple circles of partition holes on the liquid equalizing partition plate are both based on a circular topology optimization structure, significantly improving the distribution uniformity through geometric symmetry. This columnar structure enables the liquid equalizing partition plate and the liquid outlet end of the distribution body to form a columnar distribution cavity, and the multiple circles of distribution holes can be distributed in one-to-one correspondence with the multiple circles of partition holes based on the columnar distribution cavity. Under the condition of keeping the radial dimension of the distribution body unchanged, the number of branch pipes can be doubled compared with the traditional single-circle annular distribution scheme. By arranging the multiple circles of partition holes on the outer peripheral plane of the projection area of the liquid inlet hole, the dynamic blocking and reflection of the input refrigerant by the projection area are utilized to strengthen the mixing degree of the two-phase refrigerant. Combining the misalignment arrangement strategy of the multiple circles of partition holes and the liquid inlet hole, while balancing the flow resistance of each partition hole channel, it can also prevent the refrigerant from directly passing through, creating conditions for the sufficient mixing of the refrigerant before entering the multiple circles of partition holes.

[0143] Furthermore, by providing a branch pipe adapter plate at the end of the branch pipe and utilizing the transfer positioning holes distributed in a determinant pattern thereof, the end positions of the multiple circles of branch pipes distributed in an annular array on the distributor are uniformly converted into a determinant distribution adapted to the ports of the heat exchange tubes, realizing the conversion of the spatial topology structure of the connection end of the refrigerant distribution assembly. At the same time, the transfer positioning holes also achieve precise positioning of the end position of each branch pipe; during assembly, multiple branch pipes and heat exchange tubes can be assembled at one time through the branch pipe adapter plate, improving the assembly efficiency and reducing the assembly difficulty.

[0144] 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 can make some modifications and refinements without departing from the spirit and scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the scope defined by the claims.

Claims

1. A refrigerant distribution assembly for a shell and tube heat exchanger, characterized in that: include: A distributor, comprising a distribution body, a liquid equalizing baffle and a plurality of branch pipes, wherein the distribution body is in a hollow columnar shape and has a liquid inlet hole, a plurality of distribution holes and a receiving cavity; the liquid equalizing baffle is arranged in the receiving cavity along an axial direction perpendicular to the distribution body, a distribution cavity communicating with a plurality of distribution holes is formed between the liquid equalizing baffle and the liquid outlet end of the distribution body, a plurality of circles of baffle holes distributed in an annular array around the axis of the distribution body are arranged radially on the liquid equalizing baffle, and the plurality of circles of baffle holes are located on the outer peripheral plane of the projection area of ​​the liquid inlet hole on the liquid equalizing baffle; the plurality of distribution holes form a plurality of annular rows along the circumference of the distribution body, each circle of distribution holes is distributed one-to-one with the baffle holes on the corresponding circle through the distribution cavity, and the plurality of branch pipes are respectively welded in the corresponding distribution holes; A branch pipe adapter plate is arranged at the end of multiple branch pipes. The branch pipe adapter plate is formed with multiple adapter positioning holes for fixing the multiple branch pipes and distributed in a matrix manner corresponding to the ports of the heat exchange pipes in the shell and tube heat exchanger. The end of each branch pipe is inserted into the corresponding adapter positioning hole to assemble the corresponding heat exchange pipe in the shell and tube heat exchanger.

2. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 1, characterized in that: On the branch pipe adapter plate, at least a portion of the adapter positioning holes have a hole diameter that is larger than the outer diameter of the branch pipe assembled therewith.

3. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 1, characterized in that: The peripheral wall of the end of each branch pipe is sealed and welded in the transfer positioning hole, and the end of each branch pipe is used as a connecting end to be inserted into the corresponding heat exchange pipe in the shell and tube heat exchanger.

4. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 3, characterized in that: When the aperture of the adapter positioning hole is larger than the outer diameter of the corresponding branch pipe, the branch pipe adapter plate further comprises an adjustment sleeve sleeved on the outer peripheral wall of the branch pipe and inserted into the adapter positioning hole, and the branch pipe is sealed and welded in the adapter positioning hole via the adjustment sleeve.

5. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 1, characterized in that: Each branch pipe is limited in the transfer positioning hole, and the end of each branch pipe extends out of the transfer positioning hole to form a connection end for welding and connecting the corresponding heat exchange pipe in the shell and tube heat exchanger.

6. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 1, characterized in that: The multiple baffle holes on each circle are evenly spaced in an equal center distance manner. The center distance between two adjacent baffle holes on the i-th circle is L. i , the center distance between two adjacent partition holes on the jth circle is L j , the difference between the center distances of any two circles of partition holes △L ij =|L i -L j ∣≤1.2mm.

7. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 1, characterized in that: On the side of the branch pipe adapter plate close to the distribution body, a bend is formed on at least a portion of the branch pipe. When the bending angle at the bend is greater than or equal to 10 degrees, the length L of the straight pipe section from the upstream end of the bend to the end of the branch pipe inserted into the distribution hole is ≥8mm.

8. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 7, characterized in that: The distributor also includes a straight pipe sleeve which is outer-mounted on the straight pipe section and inserted into the distribution hole. The bending portion on the branch pipe is located at the downstream end of the straight pipe sleeve. When the bending portion is formed, the length of the straight pipe section is determined based on the straight pipe sleeve.

9. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 1, characterized in that: The partition hole is a through hole or a flanged hole extending toward the distribution chamber, and the aperture of the partition hole is substantially uniform or gradually decreases along the extending direction; Alternatively, the partition hole is an arc bubble hole with the hole wall protruding in an arc shape toward one side or both sides of the liquid-distributing partition.

10. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 1, characterized in that: The liquid balancing partition is a plate structure with both sides being nearly planar; or, the projection area of ​​the liquid inlet hole on the liquid balancing partition protrudes toward one side of the liquid balancing partition, and the shape of the protruding longitudinal section contour line is one or more combinations of square, trapezoid, triangle or partial circle.

11. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 1, characterized in that: The distributor also includes a flow guide member arranged in the distribution chamber and located at the inner periphery of the multiple-circle distribution holes. An annular flow channel communicating with the multiple-circle distribution holes is formed between the flow guide member and the peripheral wall of the distribution body.

12. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 11, characterized in that: The flow guide is a cylindrical spacer sleeve, one end of which abuts against the liquid-distributing spacer region on the inner periphery of the multiple-circle spacer hole, and the other end abuts against the liquid outlet end of the distribution body on the inner periphery of the multiple-circle distribution hole; Alternatively, the guide member is a guide cone, the bottom of which is arranged at the liquid outlet end of the distribution body on the inner circumference of the multiple-circle distribution holes, and the end of which extends toward the liquid equalizing partition.

13. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 10 or 12, characterized in that: The projection area of ​​the liquid inlet hole on the liquid balancing partition protrudes into the distribution cavity and abuts against the liquid outlet end of the distribution body to form a mixing cavity; the radial spacing L1 from the outer peripheral wall of the mixing cavity to the inner edge of the innermost circle distribution hole satisfies: L1≤4mm; Alternatively, the radial distance L1' from the outer peripheral wall of the spacer to the inner edge of the innermost ring distribution hole satisfies: L1'≤4mm; The inner edge of the innermost circle distribution hole refers to: at the liquid outlet end of the distribution body, the intersection of the line connecting the center of the innermost circle distribution hole and the center of the liquid outlet end of the distribution body and the edge of the innermost circle distribution hole.

14. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 1, characterized in that: The distributor further comprises a jet component arranged in the distribution chamber, wherein a jet hole is formed on the jet component and the jet hole is opposite to a projection area of ​​the liquid inlet hole on the liquid equalizing partition plate.

15. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 14, characterized in that: The distributor also includes a reflective mixing guide plate disposed in the distribution chamber and located downstream of the jet element, wherein the reflective mixing guide plate has a plurality of circles of guide holes corresponding to the plurality of distribution holes and distributed in a ring array, and the plurality of circles of guide holes are distributed on the outer peripheral plane of the projection area of ​​the jet hole on the reflective mixing guide plate; And / or, the distributor further comprises a flow guide member arranged in the distribution chamber and located downstream of the jet member, the flow guide member is located at the inner periphery of the multiple circles of distribution holes, and an annular flow channel connecting the multiple circles of distribution holes is formed between the flow guide member and the peripheral wall of the distribution body.

16. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 14, characterized in that: When the projection area of ​​the liquid inlet hole on the liquid balancing partition protrudes toward the side where the ejection component is located, the distributor also includes a partition plate arranged between the liquid balancing partition and the ejection component, and the partition plate divides the flow type maintaining cavity enclosed by the liquid balancing partition and the ejection component into a first maintaining cavity and a second maintaining cavity, and a plurality of partition plate through holes connecting the first maintaining cavity and the second maintaining cavity are formed on the partition plate; wherein, the pre-rectifying cavity volume V1, the first maintaining cavity volume V21 and the second maintaining cavity volume V22 enclosed by the liquid balancing partition and the liquid inlet end of the distribution body satisfy the following conditions: 0.75≤V1 / V21≤1.3, 0.75≤V21 / V22≤1.

3.

17. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 1, characterized in that: The distributor also includes a liquid inlet pipe welded to the liquid inlet hole, the liquid inlet pipe has a main section with a basically constant inner diameter and a jet section located downstream of the main section and with an inner diameter reduced relative to the main section, the jet section is a straight section with an inner diameter reduced relative to the main section or a Venturi tube section with a jet throat.

18. The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 1, characterized in that: The branch pipe is an integral pipe with a substantially uniform inner diameter; or, the branch pipe includes a connecting pipe section and a branch pipe extension section, and the inner diameter of the connecting pipe section is greater than or equal to the inner diameter of the branch pipe extension section.

19. A shell and tube heat exchanger, characterized in that: The invention comprises a heat exchanger shell and a tube-pass component arranged in the heat exchanger shell, wherein the tube-pass component comprises: Multiple heat exchange tubes; The refrigerant distribution assembly for a shell and tube heat exchanger according to claim 1, wherein the multiple branch pipes on the distributor are respectively sealed and connected to the multiple heat exchange tubes via branch pipe adapter plates.

20. The shell and tube heat exchanger according to claim 19, characterized in that The tube-pass assembly also includes a tube sheet, and the plurality of heat exchange tubes are sequentially assembled in a plurality of tube sheet assembly holes distributed in rows and columns on the tube sheet. A tube box is formed between the tube sheet and the end cover of the heat exchanger shell. The branch pipe adapter plate is arranged in the tube box, and its outer periphery is seal-welded to the tube sheet to form a sealed cavity between the two. The peripheral wall of each branch pipe is seal-welded in the adapter positioning hole, and the end of each branch pipe is inserted into the corresponding heat exchange tube on the tube sheet assembly hole at the sealed cavity.

21. The shell and tube heat exchanger according to claim 19, characterized in that Each branch pipe is located in the transfer positioning hole, and its end extends out of the transfer positioning hole and is sealed and connected to the corresponding heat exchange pipe by welding.

22. The shell and tube heat exchanger according to claim 19, characterized in that The distribution body is arranged in the heat exchanger shell along a direction substantially parallel to the axial direction of the heat exchanger shell; Alternatively, the distribution body is arranged in the heat exchanger shell in a direction substantially perpendicular to the axial direction of the heat exchanger shell, and each branch pipe is bent so that its end is inserted into the transfer positioning hole on the branch pipe transfer plate.

23. The shell and tube heat exchanger according to claim 19, characterized in that The heat exchange tubes are U-shaped tubes, and the tube-pass assembly includes a plurality of shell-and-tube heat exchanger refrigerant distribution assemblies arranged at the same end of the heat exchanger shell; Alternatively, the heat exchange tubes are straight tube arrays, and the tube-side components include a shell-and-tube heat exchanger refrigerant distribution component arranged at one end of the heat exchanger shell and another shell-and-tube heat exchanger refrigerant distribution component arranged at the other end of the heat exchanger shell.

24. A refrigeration device, characterized in that: Includes the shell and tube heat exchanger as described in claim 19.

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