Refrigerant distributor with aluminum legs, heat exchange assembly and refrigeration system

Abstract

The utility model provides a kind of refrigerant distributor with aluminium branch pipe, heat exchange assembly and refrigeration system, and the refrigerant distributor with aluminium branch pipe includes body assembly and multiple aluminium branch pipes.Body assembly includes steel body and multiple steel short pipes, and multiple steel short pipes are respectively arranged in multiple liquid outlet holes of steel body.Multiple aluminium branch pipes are respectively welded in the downstream end of multiple steel short pipes.In multiple aluminium branch pipes, at least one aluminium branch pipe includes transmission section, assembly section and jet portion, jet portion is arranged near or downstream side of the downstream end of transmission section to accelerate refrigerant, jet throat is formed at the minimum inner diameter of jet portion, the inner diameter of jet throat is less than the inner diameter at the downstream end of transmission section, and the inner diameter difference Δd of jet throat and the downstream end of transmission section satisfies:0.03mm≤Δd≤1.65mm;Assembly section is connected to transmission section or jet portion to match external pipeline welding.

Description

Technical Field

[0001] This utility model relates to the field of refrigeration accessories, and in particular to a refrigerant distributor, heat exchange component and refrigeration system with aluminum branch pipes. Background Technology

[0002] The continued rise in copper prices has gradually squeezed the profit margins of refrigeration equipment, forcing the refrigeration industry to seek steel and aluminum alternatives to copper to reduce material costs. Heat exchangers are key components of air conditioning units, accounting for more than 25% of the total cost. To reduce material costs, aluminum heat exchangers are now appearing on the market, and experiments have shown that aluminum and copper heat exchange tubes of the same specifications have little difference in heat exchange performance.

[0003] A refrigerant distributor is a component connected to the front end of a heat exchanger, uniformly distributing the refrigerant, after being throttled by the expansion valve, within the heat exchanger. To match and weld with aluminum heat exchangers, some have proposed all-aluminum refrigerant distributors (such as Chinese patent CN106537067A). Although aluminum has a significant cost advantage, its corrosion resistance is far lower than that of copper and steel. Aluminum not only exhibits poor corrosion resistance in strong acid and alkali environments but also suffers from galvanic corrosion when in direct contact with precious metals (especially copper), as well as weld cracking and stress corrosion due to tensile stress after welding. In Chinese patent CN106537067A, the all-aluminum refrigerant distributor is constructed by welding multiple aluminum components, resulting in multiple welds. The more welds there are, the greater the risk of leakage due to stress corrosion and weld corrosion, posing a potentially fatal safety hazard to the refrigeration equipment. Furthermore, although aluminum heat exchangers are being used at the rear end of the refrigerant distributor, the refrigeration equipment piping at the front end remains primarily copper. When the aluminum inlet section is directly welded to the copper pipe, a potential difference of nearly 2.01V will be formed between the two. In an electrolyte environment, a galvanic cell effect will occur between the copper and aluminum. The aluminum inlet section with the lower potential will act as the anode and undergo an oxidation reaction, leading to ion dissolution and galvanic corrosion, which will seriously affect the strength and service life of the copper-aluminum connection.

[0004] In addition, existing refrigerant distributors, whether made of copper or all-aluminum, suffer from the following problem: the uniformity of liquid distribution gradually deteriorates due to the difference in heat exchange capacity of each heat exchange tube in the downstream heat exchanger. The deterioration of liquid distribution performance further increases the difference in heat exchange capacity, creating a vicious cycle that seriously affects heat exchange performance. Utility Model Content

[0005] In order to overcome the shortcomings of the prior art, this utility model provides a refrigerant distributor, heat exchange component and refrigeration system with aluminum branch pipes that has excellent liquid distribution performance and good corrosion resistance.

[0006] To achieve the above objectives, the first aspect of this utility model provides a refrigerant distributor with aluminum branch pipes, comprising a main body assembly and multiple aluminum branch pipes. The main body assembly includes a steel body and multiple steel short connecting pipes, which are respectively disposed at multiple liquid outlet holes of the steel body. The multiple aluminum branch pipes are respectively welded to the downstream ends of the multiple steel short connecting pipes. Among the multiple aluminum branch pipes, at least one aluminum branch pipe includes a transmission section, an assembly section, and a jet section. The jet section is disposed near or downstream of the downstream end of the transmission section to accelerate the refrigerant. A jet throat is formed at the minimum inner diameter of the jet section. The inner diameter of the jet throat is smaller than the inner diameter at the downstream end of the transmission section, and the difference Δd between the inner diameter of the jet throat and the inner diameter at the downstream end of the transmission section satisfies: 0.03mm ≤ Δd ≤ 1.65mm. The assembly section is connected to the transmission section or the jet section to match the welding of external pipelines.

[0007] According to an embodiment of the first aspect of the present invention, an aluminum branch pipe is sleeved on the outside of the downstream end of a corresponding steel short pipe, and the two are brazed together at the sleeve joint.

[0008] According to an embodiment of the first aspect of the present invention, the assembly section is located between the transmission section and the jet section; the transmission section, the assembly section and the jet section are arranged sequentially along the transmission direction of the refrigerant and are integrally formed.

[0009] According to an embodiment of the first aspect of the present invention, the axial length L1 of the jet section is ≤350mm.

[0010] According to an embodiment of the first aspect of the present invention, the outer diameter of the assembly section is larger than the outer diameter of the transmission section to match the welding of the external pipeline, the length L2 of the assembly section is less than or equal to 35 mm, and the axial length of the assembly section refers to the total axial length from its upstream end face to its downstream end face.

[0011] According to one embodiment of the first aspect of the present invention, the assembly section is welded to the downstream end of the transmission section, and the jetting part is located inside the assembly section and is integrally formed or welded to the downstream end of the transmission section; or, the jetting part is embedded in the assembly section or the downstream end of the transmission section.

[0012] According to an embodiment of the first aspect of the present invention, the assembly section is integrally formed at the downstream end of the transmission section, and the jetting part is embedded and welded to the downstream end of the transmission section or within the assembly section.

[0013] According to an embodiment of the first aspect of the present invention, the jetting section is disposed between the transmission section and the assembly section, and the two ends of the jetting section are respectively welded to the transmission section and the assembly section;

[0014] Alternatively, the jet section may be integrally formed with at least one of the transmission section and the assembly section.

[0015] According to an embodiment of the first aspect of the present invention, the aluminum branch pipe further includes an outer sleeve welded to the assembly section, the outer sleeve being configured to increase the outer diameter at the assembly section to match the welding of the external pipeline.

[0016] According to one embodiment of the first aspect of the present invention, the jetting part is an integrally formed or sleeved jetting nozzle; or, the jetting part is an embedded jetting orifice plate.

[0017] According to an embodiment of the first aspect of the present invention, a steel short pipe is welded to the liquid outlet hole on the steel body;

[0018] Alternatively, the steel short connector can be integrally formed on the steel body around the corresponding liquid outlet.

[0019] The second aspect of this utility model also provides a heat exchange assembly, which includes an aluminum heat exchanger and the aforementioned refrigerant distributor with aluminum branch pipes, wherein the assembly section of the aluminum branch pipes is welded to the heat exchange tubes within the aluminum heat exchange assembly.

[0020] A third aspect of this utility model also provides a refrigeration system, which includes the above-mentioned heat exchange components.

[0021] In summary, the refrigerant distributor with aluminum branch pipes provided by this utility model has its main body made of steel. The refrigerant distributor as a whole only forms an aluminum weld at the connection between the aluminum branch pipe and the steel short connecting pipe. The remaining components within the steel body can be formed with high-strength, corrosion-resistant welds using oxygen-free copper brazing or self-fusion welding. Compared to an all-aluminum structure, the refrigerant distributor provided by this utility model significantly reduces the number of aluminum welds with weak corrosion resistance, greatly reducing the risk of leakage while matching the downstream aluminum heat exchanger assembly. Furthermore, the tensile strength of steel is much higher than that of aluminum, and using steel for the main body will provide higher load-bearing capacity. The steel short connecting pipe serves two purposes: firstly, it reduces the heat capacity difference between the pipes on both sides of the aluminum weld, allowing the brazing equipment to heat the pipes evenly, effectively preventing overheating and clogging of the outlet hole by the brazing filler metal; secondly, it provides conditions for the outer casing assembly of the aluminum branch pipe, creating compressive stress at the aluminum weld after welding, effectively preventing weld cracking and stress corrosion caused by tensile stress, thereby improving welding performance. Furthermore, a jet section is installed at the end of the aluminum branch pipe to significantly increase the kinetic energy of the gas-liquid two-phase refrigerant, thereby overcoming the flow resistance caused by the volume expansion of the refrigerant phase change in the downstream heat exchange tubes. This ensures that the uniformity of refrigerant distribution is not affected by the difference in downstream heat exchange, and that it can always be evenly distributed to each heat exchange tube to improve the system's heat exchange efficiency.

[0022] To make the above and other objects, features and advantages of this utility model more apparent and understandable, preferred embodiments are described below in detail with reference to the accompanying drawings. Attached Figure Description

[0023] Figure 1The image shows a refrigerant distributor with aluminum branch pipes provided in Embodiment 1 of this utility model.

[0024] Figure 2 As shown Figure 1 Assembly diagram of steel short connecting pipe and aluminum branch pipe.

[0025] Figure 3 As shown Figure 2 A partial schematic diagram of the aluminum branch pipe.

[0026] Figure 4 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0027] Figure 5 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0028] Figure 6 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0029] Figure 7 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0030] Figure 8 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0031] Figure 9 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0032] Figure 9A The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0033] Figure 10 As shown Figure 1 A schematic diagram of a refrigerant distributor with aluminum branch pipes assembled on the liquid inlet side pipeline.

[0034] Figure 11 The diagram shown is a structural schematic of a refrigerant distributor with aluminum branch pipes according to another embodiment of the present invention.

[0035] Figure 12 The diagram shown is a structural schematic of a refrigerant distributor with aluminum branch pipes according to another embodiment of the present invention.

[0036] Figure 13 The diagram shown is a structural schematic of a refrigerant distributor with aluminum branch pipes according to another embodiment of the present invention.

[0037] Figure 14 The diagram shown is a structural schematic of a refrigerant distributor with aluminum branch pipes according to another embodiment of the present invention.

[0038] Figure 15 The diagram shown is a structural schematic of a refrigerant distributor with aluminum branch pipes according to another embodiment of the present invention.

[0039] Figure 16 The diagram shown is a structural schematic of a refrigerant distributor with aluminum branch pipes according to another embodiment of the present invention.

[0040] Figure 17 The diagram shown is a structural schematic of a refrigerant distributor with aluminum branch pipes according to another embodiment of the present invention.

[0041] Figure 18 The diagram shown is a structural schematic of a refrigerant distributor with aluminum branch pipes according to another embodiment of the present invention.

[0042] Figure 19 The diagram shown is a structural schematic of a refrigerant distributor with aluminum branch pipes according to another embodiment of the present invention.

[0043] Figure 20 The diagram shown is a structural schematic of a refrigerant distributor with aluminum branch pipes according to another embodiment of the present invention.

[0044] Figure 21 The diagram shown is a structural schematic of a refrigerant distributor with aluminum branch pipes according to another embodiment of the present invention.

[0045] Figure 22 The diagram shown is a structural schematic of a refrigerant distributor with aluminum branch pipes according to another embodiment of the present invention.

[0046] Figure 23 The diagram shown is a structural schematic of a refrigerant distributor with aluminum branch pipes according to another embodiment of the present invention.

[0047] Figure 24 The diagram shown is an assembly diagram of the steel short pipe and the aluminum branch pipe in the refrigerant distributor with aluminum branch pipe provided in Embodiment 2 of this utility model.

[0048] Figure 25 As shown Figure 24 A partial schematic diagram of the aluminum branch pipe.

[0049] Figure 26 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0050] Figure 27 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0051] Figure 28The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0052] Figure 29 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0053] Figure 30 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0054] Figure 31 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0055] Figure 32 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0056] Figure 33 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0057] Figure 34 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0058] Figure 35 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0059] Figure 36 The diagram shown is a partial schematic of the aluminum branch pipe in Embodiment 3 of this utility model.

[0060] Figure 37 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0061] Figure 38 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0062] Figure 39 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0063] Figure 40 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0064] Figure 41 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0065] Figure 42 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0066] Figure 43 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0067] Figure 44 The diagram shown is a partial schematic of the aluminum branch pipe in Embodiment 4 of this utility model.

[0068] Figure 45 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0069] Figure 46 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model.

[0070] Figure 47 The diagram shown is a partial schematic of an aluminum branch pipe in another embodiment of this utility model. Detailed Implementation

[0071] Example 1

[0072] Existing all-aluminum refrigerant distributors pose significant safety hazards due to the poor corrosion resistance of aluminum welds, their large number, potential difference corrosion caused by welding with copper pipes, and weld cracking and stress corrosion caused by the high coefficient of thermal expansion. Furthermore, the uniformity of liquid distribution is gradually worsened by the difference in heat exchange capacity among the downstream heat exchange tubes. Research has found that the heat exchange capacity of each heat exchange tube varies due to the distribution of the airflow within the heat exchanger. In tubes with high heat exchange capacity, the liquid phase rapidly transforms into a large-volume gas phase after the gas-liquid two-phase refrigerant enters. Limited by the tube space, the expanding gas phase inevitably compresses the incoming refrigerant, causing flow resistance. The stronger the heat exchange, the faster the phase change, the greater the flow resistance, and the less refrigerant flows in. Conversely, tubes with weak heat exchange capacity distribute more refrigerant due to lower phase change resistance, further worsening the uniformity of liquid distribution. This worsening of the uniformity of liquid distribution further amplifies the difference in heat exchange capacity, ultimately creating a vicious cycle. This not only severely affects the heat exchange performance of the refrigeration system, but the incomplete evaporation of the liquid refrigerant also poses a risk of liquid slugging to the compressor.

[0073] In view of this, this embodiment provides a refrigerant distributor with aluminum branch pipes that exhibits excellent dispensing performance and good corrosion resistance. For example... Figure 1As shown, the refrigerant distributor with aluminum branch pipes includes a main body assembly 100 and multiple aluminum branch pipes 200. The main body assembly 100 includes a steel body 101 and multiple steel short connecting pipes 102, which are respectively disposed at multiple liquid outlet holes 1011 of the steel body 101. The multiple aluminum branch pipes 200 are respectively welded to the downstream ends of the multiple steel short connecting pipes 102. Among the multiple aluminum branch pipes 200, at least one aluminum branch pipe 200 includes a transmission section 1, an assembly section 3, and a jet section 2. The jet section 2 is disposed near or downstream of the downstream end of the transmission section 1 to accelerate the refrigerant. A jet throat 21 is formed at the minimum inner diameter d2 of the jet section 2. The inner diameter d2 of the jet throat 21 is smaller than the inner diameter d1 at the downstream end of the transmission section 1, and the difference in inner diameter between the two, Δd (Δd = d1 - d2), satisfies: 0.03mm ≤ Δd ≤ 1.65mm. Assembly section 3 is connected to transmission section 1 or jet section 2 to match external pipeline welding.

[0074] In this application, the distinction between upstream and downstream is based on the direction of refrigerant flow. Generally, refrigerant flows from upstream to downstream, and the downstream area receives refrigerant from upstream. In refrigeration equipment, refrigerant distributors are typically installed vertically or at an angle. The liquid inlet of the refrigerant distributor is located below the liquid outlet along the direction of gravity. The inertial force of the refrigerant within the distributor overcomes gravity and flows in the opposite direction. In this case, the upstream and downstream distinction is still based on the direction of refrigerant flow.

[0075] In this application, the steel is low-carbon steel, ordinary carbon steel, stainless steel, or other alloy steel; the aluminum is aluminum or aluminum alloy. An aluminum weld refers to a weld formed by brazing aluminum materials, i.e., a metal layer formed by aluminum brazing filler metal within the weld.

[0076] The refrigerant distributor provided in this embodiment has a steel-aluminum composite structure. The main body component 100 is made of high-strength, corrosion-resistant steel, while aluminum is used only at the branch pipes. This design achieves the same metal welding with the downstream aluminum heat exchanger, significantly reducing the number of aluminum welds with weak corrosion resistance, thereby greatly improving the safety and service life of the refrigerant distributor. At the same time, the steel body 101 also forms a copper-steel weld between the liquid inlet side of the refrigerant distributor and the external copper pipeline. The potential difference between copper and steel (approximately 0.84V) is lower than the copper-aluminum potential difference (2.01V), which can effectively suppress potential difference corrosion in the electrolyte environment, thereby further improving corrosion resistance.

[0077] Regarding welding performance, the steel body 101 is significantly heavier than the aluminum branch pipe 200, resulting in a substantial difference in their heat capacities. If the aluminum branch pipe 200 is directly inserted into the outlet hole 1011 for welding, uneven heating between the steel body and the aluminum branch pipe during welding can cause some brazing filler material to overheat and flow, leading to blockage of the outlet hole 1011 and severely impacting the liquid distribution performance. Furthermore, the shrinkage of the inserted aluminum branch pipe after welding and cooling will generate tensile stress, which can easily cause weld cracking and corrosion. To address this issue, this embodiment includes multiple short steel pipes 102 in the body assembly 100. These short steel pipes 102 balance the heat capacity of the pipes on both sides of the aluminum weld during welding, preventing weld blockage due to overheating. They also provide conditions for the outer casing assembly of the aluminum branch pipe 200, ensuring that the aluminum branch pipe 200 forms compressive stress around the aluminum weld after welding, thus improving weld strength and corrosion resistance. Preferably, as... Figure 1 and Figure 2 As shown, the aluminum branch pipe 200 is sleeved on the outer downstream end of the corresponding steel short pipe 102, and the two are brazed together at the joint to form an aluminum weld. However, this utility model does not impose any limitations on this.

[0078] In this embodiment, the steel short connector 102 is a straight steel section fitted into the liquid outlet 1011. However, this utility model does not impose any limitations on this. In other embodiments, the steel short connector may also be a bent steel section. Alternatively, the steel short connector may be integrally formed into the steel body around the corresponding liquid outlet, such as by using a punching and flanging process to form an integral steel short connector around the liquid outlet.

[0079] Regarding liquid distribution performance, in the refrigerant distributor with aluminum branch pipes provided in this embodiment, the jet section 2 formed at the end of the aluminum branch pipe 200 enhances the input kinetic energy of the two-phase refrigerant through high-speed jetting. This effectively overcomes the flow resistance generated by the refrigerant phase change expansion within the downstream heat exchange tube, ensuring that the refrigerant can smoothly enter the high-efficiency heat exchange tube, thereby achieving uniform refrigerant distribution. The jet section 2 effectively suppresses the distribution deterioration cycle caused by differences in heat exchange capacity, ensuring that the distribution uniformity of each aluminum branch pipe 200 is not affected by the downstream heat exchanger, thus stably improving heat exchange performance. At the same time, the jet section 2 can also eliminate the gas-liquid two-phase separation phenomenon caused by local resistance loss, friction loss, and refrigerant expansion during refrigerant transmission within the aluminum branch pipe 200, ensuring that the refrigerant is output to the downstream heat exchange tube in a fully mixed, dispersed flow pattern to improve heat exchange efficiency.

[0080] In this embodiment, the assembly section 3 is located between the transmission section 1 and the jet section 2. Specifically, as shown... Figure 1 , Figure 2 as well as Figure 3As shown, the transmission section 1, assembly section 3, and jet section 2 are sequentially arranged and integrally formed along the refrigerant transmission direction. The jet section 2 is a jet nozzle formed downstream of the assembly section 3 and having a certain axial length. A jet throat 21 is formed at the end of the jet section 2. For ease of description, in Figure 3 The downstream end of transmission section 1 (which is also the upstream end of assembly section 3) is marked with a dashed line, and the downstream end of assembly section 3 (which is also the upstream end of jet section 2) is marked with a dotted line. However, in the actual pipe fitting, transmission section 1, assembly section 3, and jet section 2 are integrally formed, with no transition boundary at their connection points, and no... Figure 3 The dashed and dotted lines in the text.

[0081] In this embodiment, the inner diameter difference Δd between the inner diameter d1 at the downstream end of the transmission section 1 and the inner diameter d2 at the jet throat 21 is 0.8 mm. However, this utility model does not impose any limitation on this. In other embodiments, the inner diameter difference Δd can also be set to other values ​​within the range of 0.03 mm to 1.65 mm, such as 0.04 mm, 0.06 mm, 0.1 mm, 0.15 mm, 0.2 mm, 0.5 mm, 1.0 mm, 1.2 mm, 1.5 mm, or 1.6 mm, etc. Furthermore, this embodiment also effectively controls the pressure drop loss of the refrigerant on the jet section 2 by limiting the axial length L1 of the jet section 2. Preferably, the axial length L1 of the jet section 2 is set to ≤350 mm. Figure 3 In the text, the axial length L1 of the jet section 2 refers to the axial length from the dotted line to the downstream end face of the jet section 2.

[0082] Although this embodiment uses the transmission section 1, assembly section 3, and jet section 2 as an example of integral molding, this invention does not limit itself in any way. In other embodiments, such as Figure 4 and Figure 5 As shown, the assembly section 3 and the jet section 2 can also be integrally formed, with the upstream end of the assembly section 3 welded to the downstream end of the transmission section 1. Alternatively, the assembly section can be integrally formed into the transmission section, while the jet section is welded to the downstream end of the assembly section.

[0083] Furthermore, this invention does not impose any limitations on the specific structure of the jet section. In other embodiments, such as... Figure 5 As shown, a jet nozzle can also be formed at the downstream end of assembly section 3; specifically, the downstream end of assembly section 3 can be sealed and then stamped to form a jet nozzle as jet section 2. Alternatively, as Figure 6 As shown, the jet section 2 is a jet tube embedded within the assembly section 3. Alternatively, the jet section is a jet orifice plate embedded within the assembly section, with jet holes formed on the orifice plate, and a jet throat formed at the minimum inner diameter of the jet holes. The specific structure of the jet orifice plate is basically the same as the structure and its variations given in Embodiment 2 below.

[0084] In the aluminum branch pipe 200 provided in this embodiment, the jet section 2 is located downstream of the assembly section 3. When assembled with the rear heat exchange tube, the jet section 2 extends into the rear heat exchange tube along with the assembly section 3. During the process of increasing the kinetic energy of refrigerant transmission, the cooling capacity generated by the flash evaporation of liquid refrigerant in the jet section 2 can also be absorbed by the rear heat exchange tube, avoiding the loss of cooling capacity during the jetting process. Furthermore, since the jet section 2 is located downstream of the assembly section 3, the refrigerant that expands and slows down in the assembly section 3 can also be converted into high-speed refrigerant to form a jet after flowing through the jet section 2. In other words, the assembly section 3 does not need to take into account the refrigerant flow rate requirements, but only needs to consider the assembly requirements with the heat exchange tube in the rear heat exchange assembly. This setting effectively solves the problems of refrigerant expansion, slowdown, and two-phase segregation caused by the large size of the assembly section 3 in existing refrigerant distributors, and achieves decoupling of the branch pipe refrigerant transmission performance and assembly requirements. It meets the welding assembly requirements while ensuring that the flow rate and uniformity of the output refrigerant meet the requirements of the rear heat exchange tube.

[0085] In this embodiment, the outer diameter of the transmission section 1 is basically the same as the inner diameter of the downstream heat exchange tube, so the overall outer diameter of the assembly section 3 is also basically close to the outer diameter at the downstream end of the transmission section 1. However, this utility model does not impose any limitations on this. In other embodiments, such as Figure 7 As shown, the outer diameter of the assembly part 32 on the assembly section 3 used for assembling the rear heat exchange tube can also be increased by the flaring process, that is, the outer diameter of the assembly part 32 is greater than the outer diameter at the downstream end of the transmission section 1. Figure 7 The intermediate assembly section 3 includes a connecting part 31 connected to the transmission section 1 and an assembly part located downstream of the connecting part 31. Alternatively, as... Figure 8 As shown, the outer diameter of the assembly part 32 on the assembly section 3 is reduced by a necking process so that the outer diameter of the assembly part 32 is smaller than the outer diameter at the downstream end of the transmission section 1.

[0086] Limited by the material's plastic deformation capacity, Figure 7 In the aluminum branch pipe structure shown, the increase in the outer diameter of the assembly section 32 is limited. However, heat exchangers of different specifications may have different heat exchange tube sizes, with some heat exchange tubes having a diameter much larger than the outer diameter of the transmission section 1. In this case, the outer diameter of the assembly section 32, formed by plastic forming methods such as flaring or diameter-changing stretching, is difficult to weld and match with the downstream heat exchange tubes. To solve this problem, in other embodiments, the aluminum branch pipe may include an outer sleeve 4 welded to the assembly section 32. The outer sleeve 4 increases the outer diameter of the assembly section 32, allowing it to be welded and assembled with heat exchange tubes of larger diameters, such as... Figure 9 As shown. In Figure 9In this embodiment, the number of outer sleeves 4 is one. However, this utility model does not impose any limitation on this. In other embodiments, when the outer diameter at the assembly section needs to be significantly increased or the increased size is a non-standard pipe wall thickness, an aluminum branch pipe can also be provided, comprising multiple outer sleeves sequentially arranged, and each outer sleeve is a commercially available standard wall thickness pipe fitting, such as... Figure 9A As shown.

[0087] In this embodiment, as Figure 1 As shown, a liquid inlet hole 1012 is formed on the liquid inlet end of the steel body 101. The refrigerant distributor with aluminum branch pipes also includes a steel liquid inlet pipe 300 welded to the liquid inlet hole 1012. However, this utility model does not limit this. In other embodiments, the steel liquid inlet pipe may also be integrally formed on the steel body. When the external pipeline on the liquid inlet side is a copper pipeline, the steel liquid inlet pipe is inserted into or sleeved on the copper pipeline. And when the external pipeline on the liquid inlet side 700 is an aluminum pipeline, such as Figure 10 As shown, a steel inlet pipe 300 is inserted into and brazed into the aluminum pipe to create compressive stress at the weld, thereby improving the connection strength between the steel inlet pipe 300 and the aluminum pipe.

[0088] In this embodiment, the steel body 101 is a structure integrating reflection and mixing. A partition 400 is provided inside the steel body 101. A cavity 401 with an opening facing the liquid inlet 1012 is formed on the partition 400 in the area opposite to the liquid inlet 1012. The partition 400 extends protruding from the cavity 401 toward the side where the liquid outlet 1011 is located. The partition 400 divides the inner cavity of the steel body 101 into a reflection mixing region 1031 near the liquid inlet end and including the cavity 401, and a mixing distribution region 1032 near the liquid outlet end. Multiple partition holes 402 are formed on the partition 400, arranged annularly around the axis of the steel body 101 and connecting the reflection mixing region 1031 and the mixing distribution region 1032. Each partition hole 402 corresponds to one liquid outlet 1011. When projected along the axial direction of the steel body 101, these partition holes 402 are located on the outer periphery of the liquid inlet 1012. However, this invention does not impose any limitations on the structure within the steel body. Figures 11 to 23 This diagram shows a structural schematic of a steel body provided in another embodiment of the present invention.

[0089] exist Figure 11The steel body 101 contains a two-stage jet reflection and mixing component 500. The two-stage jet reflection and mixing component 500 includes a primary reflection and mixing plate 501, a secondary jet orifice plate 502, and a secondary reflection and mixing plate 503, sequentially and spaced apart within the steel body 101 along the refrigerant flow direction. The primary reflection and mixing plate 501 is positioned opposite the liquid inlet 1012 to reflect and mix the refrigerant injected into the liquid inlet pipe 300. Multiple flow holes 5011 are formed on the primary reflection and mixing plate 501. The secondary jet orifice plate 502 and the primary reflection and mixing plate 501 enclose a jet cavity 5020, and a secondary jet orifice 5021 is formed on the secondary jet orifice plate 502. The refrigerant, reflected and mixed by the primary reflection and mixing plate 501, collects in the jet cavity 5020 through the flow hole 5011 and is then jetted to the secondary reflection and mixing plate 503 through the secondary jet orifice 5021. The secondary reflective mixing plate 503 is distributed opposite to the secondary jet orifice 5021 and has multiple guide holes 5031, the same number as the liquid outlet orifice 1011. Each guide hole 5031 is substantially coaxial with the corresponding liquid outlet orifice 1011. The secondary reflective mixing plate 503 reflects and mixes the refrigerant injected into the secondary jet orifice 5021, and then distributes it to the multiple liquid outlet orifices 1011 through the guide holes 5031. Specifically, in Figure 11 In the middle, the primary reflective mixing plate 501 protrudes and extends towards the side where the secondary jet orifice plate 502 is located, opposite to the liquid inlet hole 1012, to form a primary reflective cavity 5010 with an opening facing the liquid inlet hole 1012, and a secondary reflective cavity 5030 is formed on the secondary reflective mixing plate 503.

[0090] Figure 12 and Figure 11 The structures are basically the same, the difference is: Figure 12 Within the steel body 101, a chamber partition plate 504 is also provided downstream of the primary reflective mixing plate 501. The chamber partition plate 504 divides the jet cavity 5020 into an upstream chamber 5022 and a downstream chamber 5023. The upstream chamber 5022 is an annular chamber surrounding the primary reflective concave cavity 5010, and the downstream chamber 5023 connects to the secondary jet hole 5021. The chamber partition plate 504 has partition plate through holes that are staggered from the multiple flow holes 5011 (due to viewing angle...). Figure 12 (Not shown in the image).

[0091] exist Figure 13 In the steel body 101, a flat baffle 400' and a conical flow channel forming member 600 are provided. Multiple baffle holes 402 are formed on the flat baffle 400'.

[0092] Figure 14 and Figure 13 The structures are basically the same, the difference lies in: Figure 14 In this context, the flow channel forming element 600 is a spacer whose cross-section remains essentially unchanged along its extension direction. Figure 15In the middle, the steel body 101 contains only a flat partition 400'. Figure 16 In this structure, only a flow channel forming element 600 is provided inside the steel body 101; in this structure, a Venturi section is formed on the liquid inlet pipe 300, and the throat of the Venturi section accelerates the refrigerant and jets it into the flow channel forming element 600.

[0093] Figure 17 The main body 101 made of steel has a plug-in structure; Figure 18 The main body 101 of China Steel is a Venturi structure; Figure 19 The main body 101 of China Steel is a Venturi tube structure; Figure 20 The main body 101 made of steel is a reflective structure; Figure 21 The main body 101 made of steel has an impeller-type structure; Figure 22 The main body 101 of China Steel has a conical structure. Figure 23 The steel body 101 is a pressure-drop structure. The specific structure of the steel body will not be listed in detail here. Similarly, the structure of the liquid inlet pipe is not limited in any way here.

[0094] Another aspect of this embodiment provides a heat exchange assembly, which includes an aluminum heat exchanger and the aforementioned refrigerant distributor with aluminum branch pipes, wherein the assembly section 3 of the aluminum branch pipe 200 is welded to the heat exchange tube within the aluminum heat exchange assembly.

[0095] In another aspect, this embodiment also provides a refrigeration system including the above-described heat exchange components.

[0096] Example 2

[0097] This embodiment is basically the same as Embodiment 1 and its variations, except that the distribution position of the assembly section 3 and its connection method with the jet section 2 are different. In Embodiment 1, the assembly section 3 is located between the transmission section 1 and the jet section 2; however, in this embodiment, the assembly section 3 is connected to the downstream end of the transmission section, the jet section 2 is embedded and welded to the downstream end of the transmission section 1 or inside the assembly section 3, and the outer diameter of the assembly section 3 is larger than the outer diameter of the transmission section 1 to match the welding of the external pipeline.

[0098] like Figure 24 and Figure 25As shown, in this embodiment, the assembly section 3 is welded to the downstream end of the transmission section 1. Specifically, the assembly section 3 includes a connecting part 31 and an assembly part 32 located downstream of the connecting part 31. The connecting part 31 is welded to the downstream end of the transmission section 1. The jetting part 2 is a jetting nozzle integrally formed at the downstream end of the transmission section 1. The jetting nozzle extends into the assembly section 3, and its downstream end forms a jetting throat 21. In this embodiment, the axial length L1 of the jetting part 2 refers to the axial length from the connection between the downstream end of the transmission section 1 and the jetting part 2 to the downstream end face of the jetting part 2. In this embodiment, the downstream end face of the jetting part 2 is substantially flush with the downstream end face of the assembly section 3. However, this utility model does not impose any limitation on this. In other embodiments, the downstream end of the jetting part may also be located within the assembly section or extend out of the assembly section to extend into the rear heat exchange tube.

[0099] Similar to Embodiment 1, the larger outer diameter assembly section 3 enables the welding assembly of the aluminum branch pipe 200 and the rear heat exchange tube. The jet section 2 embedded within the assembly section 3 accelerates the refrigerant, increasing the kinetic energy of the refrigerant entering the rear heat exchange tube. This overcomes the flow resistance generated by the refrigerant's phase change expansion within the rear heat exchange tube, ensuring smooth entry of the refrigerant into the high-efficiency heat exchange tube and achieving uniform refrigerant distribution. Furthermore, this embodiment sets the axial length L2 of the assembly section 3 to ≤35mm. This setting allows the high-speed refrigerant output from the jet section 2 to quickly enter the rear heat exchange assembly before it has time to expand. In this embodiment, the axial length L2 of the assembly section 3 refers to the total axial length from the upstream end face of the connecting part 31 to the downstream end face of the assembly part 32. Preferably, the axial length L2 of the assembly section 3 is approximately 15mm. However, this invention does not impose any limitation on this.

[0100] In this embodiment, the transmission section 1 is a reducing pipe with a gradually decreasing inner diameter in the refrigerant transmission direction. However, this invention does not limit the specific structure of the transmission section. In its embodiments, such as Figure 26 As shown, the inner diameter of transmission segment 1 can also remain basically unchanged.

[0101] In this embodiment, the jet section 2 is a jet nozzle with a gradually decreasing inner diameter. However, this invention does not impose any limitations on this. In other embodiments, the inner diameter of the jet nozzle may remain essentially unchanged, and the structure of the jet nozzle may also be different. Figure 27 The diagram shown is a partial schematic of an aluminum branch pipe provided in another embodiment of the present invention. In this structure, a through hole is formed at the downstream end of the transmission section 1, which serves as a jet nozzle (jet section 2).

[0102] Furthermore, this invention does not limit the connection method between the jet nozzle 2 and the transmission section 1. In other embodiments, the jet nozzle (jet nozzle 2) may also be welded to the downstream end of the transmission section 1; such as Figure 28As shown, the inner sleeve of the jet section 2 is welded to the downstream end of the transmission section 1, while the outer sleeve of the connecting part 31 on the assembly section 3 is welded to the downstream end of the transmission section 1. Alternatively, as... Figure 29 As shown, the connecting parts 31 on the jet section 2 and the assembly section 3 are respectively welded to the downstream end of the transmission section 1.

[0103] Although this embodiment uses a jet nozzle with the jet section 2 integrally formed or welded as an example, the present invention does not impose any limitations on this. In other embodiments, the jet section may also be embedded within the assembly section 3, such as a jet orifice plate embedded and welded to the assembly section 3, with jet holes 23 formed on the jet orifice plate and a jet throat 21 formed at the minimum inner diameter of the jet hole 23, such as... Figures 30 to 34 As shown. Specifically, in Figure 30 In this configuration, the jet orifice 23 is a flanged hole extending from the hole wall towards the downstream end of the assembly section 3, with the jet throat 21, having the smallest inner diameter, formed at the downstream end of the flanged hole. Alternatively, as... Figure 31 and Figure 32 As shown, the jet orifice 23 is a through hole formed based on the axial thickness of the jet orifice plate. The jet orifice 23 is a constant-diameter hole with a basically unchanged diameter, and a jet throat 21 is formed at any point on it. Alternatively, as... Figure 33 and Figure 34 As shown, the jet orifice 23 includes a jet throat 21 and a guide orifice section 22. The guide orifice section 22 is located upstream of the jet throat 21 and its diameter is larger than the diameter d2 at the jet throat 21. The guide orifice section 22 with a larger inner diameter can quickly guide the refrigerant into the jet orifice 23, thereby reducing the refrigerant transmission resistance. In addition, in other embodiments, the jet orifice can also be provided as a smooth-lined Venturi orifice to reduce jet resistance. The Venturi orifice includes a guide orifice section, a jet throat, and a diffuser orifice section distributed sequentially along the refrigerant flow direction, and the diameters of the guide orifice section and the diffuser orifice section are both larger than the diameter at the jet throat.

[0104] Figure 35 The diagram shows a partial view of an aluminum branch pipe according to another embodiment of the present invention. In this structure, the connecting portion 31 on the assembly section 3 is welded to the downstream end of the transmission section 1. The jetting portion 2 is a jetting orifice plate embedded near the downstream end of the transmission section 1. Jetting holes 23 are formed on the jetting orifice plate, and a jetting throat 21 is formed at the minimum inner diameter of the jetting holes 23. Preferably, the downstream end face of the jetting orifice plate is substantially flush with the downstream end face of the transmission section 1. Figures 30 to 34 Similarly, in this structure, the jet hole can also be a flanged hole, a constant diameter through hole, or a variable diameter through hole.

[0105] Example 3

[0106] This embodiment is basically the same as Embodiment 2 and its variations, except that the connection method of assembly section 3 is different.

[0107] like Figure 36 As shown, in this embodiment, assembly section 3 is integrally formed at the downstream end of transmission section 1. The upstream end face of assembly section 3 refers to the connection point between assembly section 3 and transmission section 1. Figure 36 The middle section is where the flare begins at assembly section 3. The jetting section 2 is embedded and welded to the downstream end of transmission section 1 or within assembly section 3. Specifically, the jetting section 2 is a jetting pipe embedded in assembly section 3 and welded to the downstream end of transmission section 1. The jetting pipe is a straight pipe with a basically uniform inner diameter, and any point on it serves as the jetting throat 21. However, this invention does not impose any limitations on this. In other embodiments, the jetting pipe may also be a variable diameter pipe, with the smallest inner diameter forming the jetting throat.

[0108] The present invention does not limit the connection method of the jet tube (jet section 2). In other embodiments, the jet section 2 may also be welded to the assembly section 3. Specifically, for example... Figure 37 As shown, the jet section 2 is a jet tube with a basically uniform inner diameter, and the outer diameter of the jet tube is basically close to the inner diameter of the assembly section 3, and the two are welded together. Alternatively, as... Figure 38 As shown, the outer diameter of the jet tube is basically close to the inner diameter of the assembly section 3, but the inner diameter of the jet tube decreases along the refrigerant transmission direction. The jet tube includes an inlet guide section 22' with a larger inner diameter and a jet throat 21. The inlet guide section 22' with a relatively larger inner diameter quickly guides the refrigerant into the jet tube to reduce the flow resistance.

[0109] Although this embodiment uses the jet section 2 as an example of a jet tube, the present invention does not limit this in any way. In other embodiments, when the assembly section 3 is integrally formed at the downstream end of the transmission section 1, the jet section 2 can also be provided as a jet orifice plate. The jet orifice plate is embedded and welded into the assembly section 3, and jet holes 23 are formed on the jet orifice plate, with a jet throat 21 formed at the minimum inner diameter of the jet holes 23. Specifically, in Figure 39 and Figure 40 In this embodiment, the jet hole 23 is a flanged hole extending from the hole wall towards the downstream end of the assembly section 3, and a jet throat 21 with the smallest inner diameter is formed at the downstream end of the flanged hole. In other embodiments, the jet hole 23 may also be a through hole formed based on the axial thickness of the jet orifice plate; the jet hole 23 is a constant diameter hole with a substantially unchanged diameter, and a jet throat 21 is formed at any point on the jet hole 23, such as... Figure 41 As shown. Alternatively, the jet orifice 23 includes a guide orifice section 22 with a larger inner diameter and a jet throat 21, as shown. Figure 42 As shown. In other embodiments, the jet orifice can also be a smooth-lined Venturi orifice to reduce jet resistance. The Venturi orifice includes a guide orifice section, a jet throat, and a diffuser orifice section distributed sequentially along the refrigerant flow direction. The diameters of the guide orifice section and the diffuser orifice section are both larger than the diameter at the jet throat.

[0110] Figure 43This is a partial schematic diagram of an aluminum branch pipe provided in another embodiment of the present invention. In this structure, the jet section 2 is also a jet orifice plate and the jet orifice plate is embedded and welded near the downstream end of the transmission section 1.

[0111] Example 4

[0112] This embodiment is basically the same as Embodiment 2 and its variations, except that: the jet section 2 is a jet pipe disposed between the transmission section 1 and the assembly section 3, and the jet section 2 is integrally formed with at least one of the transmission section 1 and the assembly section 3.

[0113] In this embodiment, as Figure 44 As shown, the jet section 2 is a variable-diameter pipe integrally formed on the upstream end of the transmission section 1, with its inner diameter gradually decreasing along the refrigerant transmission direction. A jet throat 21 is formed at the end of the jet section 2 and inserted and welded into the assembly section 3. However, this invention does not limit this aspect. In other embodiments, the upstream end of the jet section 2 may be welded to the transmission section 1, while its downstream end is integrally formed with the assembly section 3, such as... Figure 45 As shown. Alternatively, the transmission section 1, the jet section 2, and the assembly section 3 are sequentially distributed along the refrigerant transmission direction and integrally formed, as shown. Figure 46 As shown. Alternatively, the two ends of the jet section 2 are welded to the transmission section 1 and the assembly section 3, respectively, as shown. Figure 47 As shown.

[0114] In summary, the refrigerant distributor with aluminum branch pipes provided by this utility model has its main body made of steel. The refrigerant distributor as a whole only forms an aluminum weld at the connection between the aluminum branch pipe and the steel short connecting pipe. The remaining components within the steel body can be formed with high-strength, corrosion-resistant welds using oxygen-free copper brazing or self-fusion welding. Compared to an all-aluminum structure, the refrigerant distributor provided by this utility model significantly reduces the number of aluminum welds with weak corrosion resistance, greatly reducing the risk of leakage while matching the downstream aluminum heat exchanger assembly. Furthermore, the tensile strength of steel is much higher than that of aluminum, and using steel for the main body will provide higher load-bearing capacity. The steel short connecting pipe serves two purposes: firstly, it reduces the heat capacity difference between the pipes on both sides of the aluminum weld, allowing the brazing equipment to heat the pipes evenly, effectively preventing overheating and clogging of the outlet hole by the brazing filler metal; secondly, it provides conditions for the outer casing assembly of the aluminum branch pipe, creating compressive stress at the aluminum weld after welding, effectively preventing weld cracking and stress corrosion caused by tensile stress, thereby improving welding performance. Furthermore, a jet section is installed at the end of the aluminum branch pipe to significantly increase the kinetic energy of the gas-liquid two-phase refrigerant, thereby overcoming the flow resistance caused by the volume expansion of the refrigerant phase change in the downstream heat exchange tubes. This ensures that the uniformity of refrigerant distribution is not affected by the difference in downstream heat exchange, and that it can always be evenly distributed to each heat exchange tube to improve the system's heat exchange efficiency.

[0115] Although the present invention has been disclosed above by way of preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art may make some modifications and refinements without departing from the spirit and scope of the present invention. Therefore, the scope of protection of the present invention shall be determined by the scope of protection claimed in the claims.

Claims

1. A refrigerant distributor with aluminum branch pipes, characterized in that, include: The main body assembly includes a steel body and multiple short steel pipes, with the multiple short steel pipes respectively disposed at multiple liquid outlet holes of the steel body; Multiple aluminum branch pipes are welded to the downstream ends of multiple steel short pipes; In a plurality of aluminum branch pipes, at least one aluminum branch pipe includes a transmission section, an assembly section, and a jet section. The jet section is located near or downstream of the downstream end of the transmission section to accelerate the refrigerant. A jet throat is formed at the minimum inner diameter of the jet section. The inner diameter of the jet throat is smaller than the inner diameter at the downstream end of the transmission section, and the difference Δd between the inner diameter of the jet throat and the inner diameter at the downstream end of the transmission section satisfies: 0.03mm≤Δd≤1.65mm. The assembly section is connected to the transmission section or the jet section to match the welding of external pipelines.

2. The refrigerant distributor with aluminum branch pipes according to claim 1, characterized in that, The aluminum branch pipe is sleeved onto the outside of the downstream end of the corresponding steel short pipe, and the two are brazed together at the joint.

3. The refrigerant distributor with aluminum branch pipes according to claim 1, characterized in that, The assembly section is located between the transmission section and the jet section; the transmission section, assembly section and jet section are arranged sequentially along the transmission direction of the refrigerant and are integrally formed.

4. The refrigerant distributor with aluminum branch pipes according to claim 1, characterized in that, The axial length L1 of the jet section is ≤350mm.

5. The refrigerant distributor with aluminum branch pipes according to claim 1, characterized in that, The outer diameter of the assembly section is larger than that of the transmission section to match the welding of the external pipeline. The length L2 of the assembly section is less than or equal to 35 mm. The axial length of the assembly section refers to the total axial length from its upstream end face to its downstream end face.

6. The refrigerant distributor with aluminum branch pipes according to claim 5, characterized in that, The assembly section is welded to the downstream end of the transmission section, and the jetting part is located inside the assembly section and is integrally formed or welded to the downstream end of the transmission section; or, the jetting part is embedded in the assembly section or the downstream end of the transmission section.

7. The refrigerant distributor with aluminum branch pipes according to claim 5, characterized in that, The assembly section is integrally formed at the downstream end of the transmission section, and the jetting part is embedded and welded to the downstream end of the transmission section or within the assembly section.

8. The refrigerant distributor with aluminum branch pipes according to claim 5, characterized in that, The jet section is disposed between the transmission section and the assembly section, and both ends of the jet section are welded to the transmission section and the assembly section, respectively. Alternatively, the jet section may be integrally formed with at least one of the transmission section and the assembly section.

9. The refrigerant distributor with aluminum branch pipes according to claim 1, characterized in that, The aluminum branch pipe also includes an outer sleeve welded to the assembly section, the outer sleeve being configured to increase the outer diameter at the assembly section to match the welding of external pipelines.

10. The refrigerant distributor with aluminum branch pipes according to claim 1, characterized in that, The jetting part is an integrally formed or sleeved jetting nozzle; or, the jetting part is an embedded jetting orifice plate.

11. The refrigerant distributor with aluminum branch pipes according to claim 1, characterized in that, The steel short connecting pipe is welded to the liquid outlet hole on the steel body; Alternatively, the steel short connector may be integrally formed on the steel body around the corresponding liquid outlet.

12. A heat exchange component, characterized in that, include: Aluminum heat exchanger; The refrigerant distributor with aluminum branch pipes as described in claim 1, wherein the assembly section of the aluminum branch pipes is welded to the heat exchange tubes within the aluminum heat exchange assembly.

13. A refrigeration system, characterized in that, Includes the heat exchange component as described in claim 12.

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