WO2024077737A1 - 大规格分歧管 - Google Patents

大规格分歧管 Download PDF

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Publication number
WO2024077737A1
WO2024077737A1 PCT/CN2022/135398 CN2022135398W WO2024077737A1 WO 2024077737 A1 WO2024077737 A1 WO 2024077737A1 CN 2022135398 W CN2022135398 W CN 2022135398W WO 2024077737 A1 WO2024077737 A1 WO 2024077737A1
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Prior art keywords
pipe
main pipe
branch pipe
section
extrusion
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PCT/CN2022/135398
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English (en)
French (fr)
Inventor
斯壮伟
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含山瑞可金属有限公司
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Publication of WO2024077737A1 publication Critical patent/WO2024077737A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L41/00—Branching pipes; Joining pipes to walls
    • F16L41/02—Branch units, e.g. made in one piece, welded, riveted
    • F16L41/021—T- or cross-pieces
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/18—Network design, e.g. design based on topological or interconnect aspects of utility systems, piping, heating ventilation air conditioning [HVAC] or cabling
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2113/00—Details relating to the application field
    • G06F2113/14—Pipes

Definitions

  • the invention relates to the field of air-conditioning accessories, and in particular to a large-size branch pipe.
  • a dedicated branch pipe with a diversion or confluence function is required for connection.
  • branch pipes There are currently two main types of branch pipes on the market; one is a traditional branch pipe with three welds, which is welded by a tee pipe and three extension pipes. Among them, the three connecting ends of the tee pipe are very short, and the length ratio of each connecting end is less than 2 times, so although it is easy to extrude and form, its three connecting ends are very short.
  • the inventor proposed a branch pipe in patent CN209800942U in which the pipe body is formed in one piece after extrusion.
  • the branch pipe is an integrated structure and its length is sufficient to meet the pipe connection requirements of the multi-connected air conditioner (heat pump) system, so the overall product has fewer welds and high safety performance.
  • the current high-power multi-split air conditioner (heat pump) system still uses a branch pipe with three welds 10, 20, and 30, which is easy to process and is based on a tee pipe, as shown in Figures 1 and 2; in order to more intuitively show the formation of the weld, the weld 30 is shown in a decomposed schematic manner.
  • the problem with this type of branch pipe is that the product has many welds, a high risk of leakage, and high cost.
  • the present invention provides a large-sized branch pipe that is easy to process and has high safety performance.
  • the present invention provides a large-size branch pipe, which includes an extruded main body and a main pipe connection.
  • the extruded main body is formed as a whole by extrusion of a pipe fitting, and the extruded main body includes an extruded main pipe and two branch pipes, each branch pipe has a curved section connected to the extruded main pipe, and the curved section bends and extends in a direction away from the extruded main pipe, the outer diameter of the extended end of the curved section is greater than 22 mm, and the shortest length of the two branch pipes is greater than or equal to 3 times the length of the extruded main pipe.
  • the inner sleeve of the main pipe connection is welded to the extruded main pipe; along the insertion direction of the main pipe connection, the end face of the insertion end of the main pipe connection is flush with or extends beyond the position of T min on the extruded main pipe, and the correlation coefficient K between T min and the outer diameter D of the extended end of the curved section on the branch pipe and the saturated vapor pressure of the refrigerant satisfies the following minimum wall thickness model:
  • Tmin KD-b
  • Tmin is the minimum wall thickness on the extruded main pipe when the large-size branch pipe meets the pressure test specified in GB4706.32-2012 standard
  • the refrigerant saturated vapor pressure correlation coefficient K and constant b are obtained by indexing the refrigerant saturated vapor pressure correlation coefficient table.
  • the intersection of the center line of the connecting area of the two branch pipes and the axis of the extruded main pipe is taken as the origin of the coordinate system
  • the axis of the extruded main pipe is the Y axis
  • the direction perpendicular to the Y axis is the X axis
  • the distance Ly from the end face of the main pipe insertion end to the coordinate origin satisfies the following conditions:
  • n 0 mm to 2.3 mm.
  • the welding depth of the main pipe connection is greater than or equal to 0.2 times the outer diameter of the extended end of the upper curved section of the branch pipe, and the welding depth refers to the maximum depth of the solder melt in the weld.
  • the extruded body and the main pipe connection are both made of copper material.
  • the wall thickness of the extruded body gradually decreases.
  • the wall thickness of the extruded main body is greater than or equal to the wall thickness of the end of the extended curved section of the branch pipe.
  • the ratio of the center distance between the two branch pipes to the outer diameter of the extended end of the upper curved section of the branch pipe is between 2.2 and 4 times.
  • the main pipe connection includes a pipe straight section and a pipe connecting section, the pipe straight section is partially or completely welded to the extruded main pipe, and the pipe connecting section includes at least one flared section, at least one necked section, or a combination of at least one flared section and at least one necked section.
  • each branch pipe has a connecting section
  • the connecting section includes at least one expanding section, at least one shrinking section, or a combination of at least one expanding section and at least one shrinking section.
  • the large-sized branch pipe is suitable for air-conditioning refrigeration systems using refrigerants such as R22, R32, R125, R134A, R410A, and R407C.
  • the large-sized branch pipe provided in this embodiment introduces another factor, the relationship between the end face of the main pipe insertion end and the position of T min on the extruded main pipe, on the basis of the wall thickness, which is a factor affecting the pressure resistance, to achieve dual variable adjustment of the pressure resistance performance of the large-sized branch pipe.
  • the improvement of the product pressure resistance performance brought about by the adjustment of the end face position of the main pipe insertion end provides more space for the selection of the wall thickness of the original pipe before extrusion, so that the large-sized branch pipe provided in this embodiment achieves the optimal selection of the wall thickness of the original pipe before extrusion while ensuring that the product pressure resistance performance meets the standard design requirements, greatly reducing the cost of the large-sized branch pipe.
  • FIG. 1 and FIG. 2 are schematic diagrams showing the structure of existing large-sized branch pipes.
  • FIG3 is a schematic diagram showing the structure of a large-sized branch pipe provided in one embodiment of the present invention.
  • FIG. 4 is a schematic diagram showing the structure of the test product when the data table 1 is formed through the pressure test.
  • FIG. 5 is a partial enlarged view of FIG. 4 .
  • FIG6 is a schematic partial cross-sectional view of the large-sized branch pipe shown in FIG3 near the extrusion main pipe.
  • FIG. 7 is another partial cross-sectional schematic diagram of the large-sized branch pipe shown in FIG. 3 .
  • FIG8 is a schematic diagram showing the adjustment of the end face of the insertion end of the main pipe in the large-size branch pipe shown in FIG3 .
  • FIG. 9 is a schematic diagram showing the processing flow of the large-sized branch pipe shown in FIG. 3 .
  • the current method is to increase the wall thickness of the original pipe to increase the wall thickness of the extrusion area, thereby improving the pressure resistance of this area.
  • the increase in the wall thickness of the original pipe due to the influence of the extrusion process, there is no specific relationship between the increase in the wall thickness of the original pipe and the pressure resistance performance.
  • the choice of the original pipe wall thickness is vague, and designers can usually only give a larger wall thickness based on experience to meet the pressure resistance requirements of the pipe fittings.
  • the material cost is very sensitive to the increase in the wall thickness of the original pipe. A slight increase in the wall thickness may lead to a substantial increase in material costs.
  • the present embodiment provides a large-sized branch pipe; as shown in Figures 3 to 7, the large-sized branch pipe includes an extrusion main body 1 and a main pipe pipe 2.
  • the extrusion main body 1 is formed as a whole by extrusion of a pipe fitting, and the extrusion main body 1 includes an extrusion main pipe 11 and two branch pipes, and the main pipe pipe 2 is welded to the extrusion main pipe 11.
  • Each branch pipe has a bending section connected to the extrusion main pipe 11, and the bending section bends and extends in a direction away from the extrusion main pipe.
  • the outer diameter D of the extended end of the bending section is greater than 22 mm and the length of the shorter of the two branch pipes is greater than or equal to 3 times the length of the extrusion main pipe 11.
  • the length of the branch pipe refers to the vertical distance from the intersection of the center line of the connection area of the two branch pipes and the axis of the extrusion main pipe to the end face of the branch pipe;
  • the length of the extrusion main pipe refers to the vertical distance from the intersection of the center line of the connection area of the two branch pipes and the axis of the extrusion main pipe to the end face of the extrusion main pipe.
  • the two branch pipes are respectively the first branch pipe 12 and the second branch pipe 13.
  • the first branch pipe 12 includes a first curved section 121 and a first connecting section 122 connected in sequence along its extension direction, and the first curved section 121 and the extrusion main pipe 11 are connected by a curved transition of the first transition section 141; the extended end of the first curved section 121 refers to the position where the first curved section 121 and the first connecting section 122 are connected, as shown in the P4 position in FIG3 and FIG7.
  • the second branch pipe 13 includes a second curved section 131, a second straight section 132 and a second connecting section 133 connected in sequence along its extension direction, and the second curved section 131 and the extrusion main pipe 11 are connected by a curved transition of the second transition section 142; the extended end of the second curved section 131 refers to the position where the second curved section 131 and the second straight section 132 are connected, as shown in the P4' position in FIG3 and FIG7.
  • the outer diameters D of the extending ends of the first curved section 121 and the extending ends of the second curved section 131 are substantially equal, and the wall thicknesses t of the two at the locations are also substantially equal.
  • the present invention does not impose any limitation on the specific structure of the first branch pipe 12 and the second branch pipe 13.
  • the structure of the first branch pipe may be the same as that of the second branch pipe, such as including a first curved section, a first straight section and a first connecting section connected in sequence; in this case, the end of the extension section of the first curved section refers to the connection between the first curved section and the first straight section.
  • the structure of the second branch pipe may also only include a second curved section and a second connecting section.
  • test products Eleven test groups were selected based on the outer diameter D of the extended end of the curved section on the branch pipe, and three sub-test groups were formed in each test group based on the wall thickness of the extended end of the curved section. Nine test products were formed in each sub-test group by measuring the wall thickness T1 of the extruded main pipe 11 corresponding to the end face of the insertion end of the main pipe 2 at different positions.
  • the end face of the extruded main pipe 11 was used as the reference plane in the test, and the insertion depth H of the main pipe 2 was used to characterize the position of the end face of the insertion end of the main pipe 2 on the extruded main pipe 11.
  • the outer diameter D of the extended end of the curved section on the branch pipe refers to the nominal outer diameter.
  • the outer diameter D of the extended end of the bending section in the first test group is 25mm; the wall thickness t of the extended end of the bending section in the sub-test groups contained therein is 0.85mm, 0.95mm, 1mm; the insertion depth H of the main pipe 2 in each sub-test group is 3mm, 4mm, 5mm, 6mm, 7mm, 8mm, 9mm, 10mm, 11mm.
  • the outer diameter D of the extended end of the bending section in the second test group is 28 mm; the wall thickness t of the extended end of the bending section in the sub-test groups it contains is 0.9 mm, 1 mm, 1.1 mm; the insertion depth H of the main pipe 2 in each sub-test group is 5 mm, 6 mm, 7 mm, 8 mm, 9 mm, 10 mm, 11 mm, 12 mm, 13 mm.
  • the outer diameter D of the extended end of the bending section in the third test group is 31.8 mm; the wall thickness t of the extended end of the bending section in the sub-test groups included therein is 1 mm, 1.1 mm, 1.2 mm; the insertion depth H of the main pipe 2 in each sub-test group is 5 mm, 6 mm, 7 mm, 8 mm, 9 mm, 10 mm, 11 mm, 12 mm, 13 mm.
  • the outer diameter D of the extended end of the bending section in the fourth test group is 35 mm; the wall thickness t of the extended end of the bending section in the sub-test groups included therein is 1.05 mm, 1.15 mm, 1.25 mm; the insertion depth H of the main pipe 2 in each sub-test group is 7 mm, 8 mm, 9 mm, 10 mm, 11 mm, 12 mm, 13 mm, 14 mm, 15 mm.
  • the outer diameter D of the extended end of the bending section in the fifth test group is 38 mm; the wall thickness t of the extended end of the bending section in the sub-test groups included therein is 1.15 mm, 1.25 mm, 1.35 mm; the insertion depth H of the main pipe 2 in each sub-test group is 7 mm, 8 mm, 9 mm, 10 mm, 11 mm, 12 mm, 13 mm, 14 mm, 15 mm.
  • the outer diameter D of the extended end of the bending section in the sixth test group is 42 mm; the wall thickness t of the extended end of the bending section in the sub-test groups included therein is 1.25 mm, 1.35 mm, 1.45 mm; the insertion depth H of the main pipe 2 in each sub-test group is 7 mm, 8 mm, 9 mm, 10 mm, 11 mm, 12 mm, 13 mm, 14 mm, 15 mm.
  • the outer diameter D of the extended end of the bending section in the seventh test group is 45 mm; the wall thickness t of the extended end of the bending section in the sub-test groups included therein is 1.35 mm, 1.45 mm, 1.55 mm; the insertion depth H of the main pipe 2 in each sub-test group is 7 mm, 8 mm, 9 mm, 10 mm, 11 mm, 12 mm, 13 mm, 14 mm, 15 mm.
  • the outer diameter D of the extended end of the bending section in the eighth test group is 48 mm; the wall thickness t of the extended end of the bending section in the sub-test groups included therein is 1.45 mm, 1.55 mm, 1.65 mm; the insertion depth H of the main pipe 2 in each sub-test group is 7 mm, 8 mm, 9 mm, 10 mm, 11 mm, 12 mm, 13 mm, 14 mm, 15 mm.
  • the outer diameter D of the extended end of the bending section in the ninth test group is 50.8 mm; the wall thickness t of the extended end of the bending section in the sub-test groups included therein is 1.55 mm, 1.65 mm, 1.75 mm; the insertion depth H of the main pipe 2 in each sub-test group is 9 mm, 10 mm, 11 mm, 12 mm, 13 mm, 14 mm, 15 mm, 16 mm, 17 mm.
  • the outer diameter D of the extended end of the bending section in the tenth test group is 54 mm; the wall thickness t of the extended end of the bending section in the sub-test groups included therein is 1.55 mm, 1.75 mm, 1.85 mm; the insertion depth H of the main pipe 2 in each sub-test group is 9 mm, 10 mm, 11 mm, 12 mm, 13 mm, 14 mm, 15 mm, 16 mm, 17 mm.
  • the outer diameter D of the extended end of the bending section in the eleventh test group is 63 mm; the wall thickness t of the extended end of the bending section in the sub-test groups it contains is 1.9 mm, 2.0 mm, 2.1 mm; the insertion depth H of the main pipe 2 in each sub-test group is 10 mm, 11 mm, 12 mm, 13 mm, 14 mm, 15 mm, 16 mm, 17 mm, 18 mm.
  • the overall pressure resistance of the large-sized branch pipe is related to the wall thickness T1 of the extruded main pipe 11 at the end face of the insertion end of the main pipe 2. Specifically, when the wall thickness T1 of the extruded main pipe at the end face of the insertion end of the main pipe 2 is greater than a certain wall thickness critical point Tmin, the pressure resistance of the large-sized branch pipe will meet the pressure test conditions specified in the standard GB4706.32-2012.
  • the extruded main body 1 is formed by extrusion of a pipe fitting and the extruded main pipe 11 is the extrusion end.
  • the flow compensation of the material in the extrusion process determines that the wall thickness of the extruded main pipe 11 will gradually increase along the insertion direction of the main pipe 2. Therefore, when welding and assembling the main pipe 2, it is only necessary to control the position of the insertion end face of the main pipe 2 so that it is flush with or extends over the position of Tmin on the extruded main pipe to ensure that the overall pressure resistance performance of the large-sized branch pipe meets the pressure test conditions specified in the standard GB 4706.32-2012.
  • the Tmin on the extruded main pipe 11 Since the location of Tmin on the extruded main pipe is the positioning basis of the end face of the insertion end of the main pipe 2 when welding, when designing a large-size branch pipe, for a given outer diameter D of the extended end of the curved section on the branch pipe, the Tmin on the extruded main pipe 11 needs to be determined first.
  • the Tmin of the extruded main pipe 11 in each test group in Table 1 is summarized to form Table 2. After further analysis of Table 2, it is found that: in each experimental group, the Tmin on the extruded main pipe 11 is related to the outer diameter D of the extended end of the curved section, and the two are in a certain linear relationship.
  • Tmin is the minimum wall thickness on the extruded main pipe 11 when the large-size branch pipe meets the pressure test specified in the standard GB 4706.32-2012
  • the refrigerant saturated vapor pressure correlation coefficient K and the constant b can be obtained by indexing the refrigerant saturated vapor pressure correlation coefficient table (i.e., Table 4).
  • Formula 1 and Table 4 are established so that the large-size branch pipe provided in this embodiment can be designed based on the outer diameter D of the extended end of the curved section of the given branch pipe and the type of refrigerant used in the air conditioning system to calculate Tmin on the extruded main pipe 11.
  • Tmin on the extruded main pipe 11 is calculated according to Formula 1 and Table 4, it can fluctuate up and down by 3%.
  • the intersection of the center line of the connecting area of the two branch pipes and the axis of the extrusion main pipe 11 is taken as the origin O of the coordinate system
  • the axis of the extrusion main pipe 11 is taken as the Y axis
  • the direction perpendicular to the Y axis is taken as the X axis to construct a rectangular coordinate system.
  • D is the outer diameter of the extended end of the curved section on the branch pipe, which is the outer diameter at position P4 and P4' in Figure 7;
  • t is the wall thickness of the extended end of the curved section, which is the wall thickness at position P4 and P4' in Figure 7;
  • n 0mm ⁇ 4.5mm.
  • the present invention does not impose any limitation on this; in other embodiments, the upper limit of n can be selected from other values within the range of 0mm ⁇ 4.5mm.
  • ⁇ is set as a constant with a certain correction range.
  • the large-sized branch pipe provided in this embodiment only needs to control the distance L y ⁇ ⁇ D-t+n from the position P2 of the end face of the insertion end of the main pipe 2 to the coordinate origin O, so that the overall pressure resistance of the large-sized branch pipe shown in Figure 3 can meet the standard requirements.
  • Formula 1 is used to predict Tmin on the extruded main pipe 11. Afterwards, the selection of the wall thickness of the original pipe before the extrusion process is guided by the predicted Tmin , and the original pipe wall thickness with the best economic efficiency is selected for extrusion under the premise of ensuring that Tmin exists on the extruded main pipe 11 after extrusion.
  • L min and L max can be directly determined based on the outer diameter D of the extended end of the upper curved section of the branch pipe and the wall thickness t therein, which makes product design convenient and unaffected by measurement errors.
  • the present invention does not make any limitation to this.
  • the position of T min can also be marked on the extruded main pipe by measuring the extruded sample multiple times.
  • the welding depth after welding of the two also needs to be considered during assembly.
  • the welding depth after welding the main pipe 2 and the extruded main pipe 11 is set to be greater than or equal to 0.2 times the outer diameter D of the extended end of the bending section, and the welding depth refers to the maximum depth of the solder molten depth in the weld, as shown by the distance L in FIGS. 5 and 6 .
  • the extruded body 1 and the main pipe 2 are both made of copper and the ratio of the center distance between the two branch pipes to the outer diameter D of the upper curved section of the branch pipe is between 2.2 and 4 times.
  • the present invention does not make any limitation to this.
  • the main pipe 2 includes a pipe straight section 21 and a pipe connecting section 22.
  • the pipe straight section 21 is partially welded to the extruded main pipe 11, and the pipe connecting section 22 includes two expanding sections with gradually increasing outer diameters.
  • the pipe straight section may also be completely sleeved to the extruded main pipe; or, the pipe connecting section may also include one or more than three expanding sections, at least one shrinking section, or a combination of at least one expanding section and at least one shrinking section.
  • the first connecting section 122 on the first branch pipe 12 also includes two expanding sections with gradually increasing outer diameters.
  • the second connecting section 133 on the second branch pipe 13 also includes two expanding sections with gradually increasing outer diameters.
  • the present invention does not impose any limitation on this.
  • the first connecting section and the second connecting section may also include one or more expanding sections, at least one shrinking section, or a combination of at least one expanding section and at least one shrinking section.
  • the large-sized branch pipe provided in this embodiment introduces another factor, the relationship between the end face of the main pipe insertion end and the position of T min on the extruded main pipe, on the basis of the wall thickness, which is a factor affecting the pressure resistance, to achieve dual variable adjustment of the pressure resistance performance of the large-sized branch pipe.
  • the improvement of the product pressure resistance performance brought about by the adjustment of the end face position of the main pipe insertion end provides more space for the selection of the wall thickness of the original pipe before extrusion, so that the large-sized branch pipe provided in this embodiment achieves the optimal selection of the wall thickness of the original pipe before extrusion while ensuring that the product pressure resistance performance meets the standard design requirements, greatly reducing the cost of the large-sized branch pipe.
  • the units of the outer diameter D of the extended end of the curved section, the wall thickness t of the extended end of the curved section, the insertion depth H, and the wall thickness T1 of the extruded main pipe at the end surface of the extruded main pipe insertion end in the test product are all mm.

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Abstract

一种大规格分歧管，包括挤压主体（1）和主管接管（2），挤压主体由一根管件经挤压后一体成型，挤压主体包括挤出主管（11）和两根分流支管，每一分流支管均具有连通挤出主管的弯曲段且弯曲段向远离挤出主管的方向弯曲延伸，弯曲段延伸末端的外径大于22毫米且两根分流支管的最短长度大于或等于挤出主管长度的3倍，主管接管内套焊接于挤出主管；沿主管接管的插入方向，主管接管的插入端端面平齐于或延伸过挤出主管上T min所在的位置，最小壁厚T min与分流支管上弯曲段延伸末端的外径D以及制冷剂饱和蒸汽压力相关系数K满足最小壁厚模型。该大规格分歧管在保证产品耐压性能满足标准设计要求的前提下实现了挤压前原始管件壁厚的最优选择，降低了大规格分歧管的成本。

Description

大规格分歧管 技术领域
本发明涉及空调配件领域，且特别涉及一种大规格分歧管。
背景技术
在多联式空调(热泵)机组中，为实现管道中制冷剂的分配，需要采用专用的且具有分流或合流作用的分歧管进行连接。目前市面上的分歧管主要有两种；一种是传统的具有三条焊缝的分歧管，其由三通管和三根延长管焊接而成。其中，三通管的三个连接端长度均很短，各连接端长度比在2倍以下，所以虽然容易挤压成型，但是其三个连接端均很短，它若直接与多联式空调(热泵)系统上的配管焊接时热量的传递极易导致焊缝的二次熔化而产生泄漏；此外，由于三通管的三个连接端的端口尺寸均固定，所以无法与空调系统管路上多种尺寸的配管相连接。因此，需要在三个连接端上焊接延长管以解决焊缝二次熔化和多尺寸规格配管的连接问题。而三根延长管的焊接使得这类分歧管存在焊缝过多、泄漏隐患大、铜材浪费以及成本高等问题。
为了解决市场上以三通管为主体的具有三条焊缝的分歧管泄漏投诉多的问题，发明人于专利CN209800942U中提出了一种管体经挤压后一体成型的分歧管，在该结构中支管为一体式结构且其长度足以满足多联式空调(热泵)系统的管路连接要求，故产品整体的焊缝少、安全性能高。然而，当这种结构的大规格分歧管应用于制冷功率较大的多联式空调(热泵)系统时，管径的增大使得挤压成型时产品和模具间摩擦面积过大，材料难以流动至挤出端，进而导致主管挤出区域成为产品耐压的薄弱区域；于此同时，管径的增大也势必带来产品耐压性能的降低。为保证大规格的这类分歧管的耐压强度，当前本领域技术人员只能通过不断增加原始管材壁厚来提升主管挤压区域的耐压性能。而铜作为一种贵金属材料，管材壁厚的增加势必导致成本的大幅度提升，对于大管径产品而言成本的提升尤为显著。
基于大规格的管体经挤压后一体成型的分歧管所存在的挤压困难和成本高等问题，当前大功率的多联式空调(热泵)系统仍然采用加工容易的以三通管为主体的具有三条焊缝 10,20,30的分歧管，如图1和图2所示；为更直观的表示焊缝的形成，焊缝30处采用分解示意的方式进行表示。但如前文所述，这类分歧管的问题在于产品焊缝多，泄漏隐患大，成本高等问题。
发明内容
本发明为了克服现有技术的至少一个不足，提供一种易加工且安全性能高的大规格分歧管。
为了实现上述目的，本发明提供一种大规格分歧管，其包括挤压主体和主管接管。挤压主体由一根管件经挤压后一体成型，挤压主体包括挤出主管和两根分流支管，每一分流支管均具有连通挤出主管的弯曲段且弯曲段向远离挤出主管的方向弯曲延伸，弯曲段延伸末端的外径大于22毫米且两根分流支管的最短长度大于或等于挤出主管长度的3倍。主管接管内套焊接于挤出主管；沿主管接管的插入方向，主管接管的插入端端面平齐于或延伸过挤出主管上T min所在的位置，T min与分流支管上弯曲段延伸末端的外径D以及制冷剂饱和蒸汽压力相关系数K满足以下最小壁厚模型：
T min＝KD-b；
其中，T min为大规格分歧管满足GB4706.32-2012标准所规定的压力测试试验时挤出主管上的最小壁厚，制冷剂饱和蒸汽压力相关系数K和常数b通过索引制冷剂的饱和蒸汽压力相关系数表所得。
根据本发明的一实施例，以两根分流支管连通区的中心线和挤出主管轴线的交点作为坐标系原点，挤出主管轴线为Y轴，垂直于Y轴的方向为X轴；在Y轴方向上，主管接管插入端端面至坐标原点的距离L y满足以下条件：
L y∈[L min,L max]；
L min＝D/2-t；
L max＝αD-t+n；
其中，L max指的是：在Y轴方向上，T min所在的位置至坐标原点的距离；D为分流支管上弯曲段延伸末端的外径；t弯曲段延伸末端的壁厚；α为一常数且α＝0.56～0.8；n＝0mm～4.5mm。
根据本发明的一实施例，主管接管插入端端面至坐标原点的距离L y所需满足的L max中，n＝0mm～2.3mm。
根据本发明的一实施例，主管接管的焊接深度大于等于分流支管上弯曲段延伸末端外径的0.2倍，焊接深度指的是焊缝内焊料熔深的最大深度。
根据本发明的一实施例，挤压主体和主管接管均为铜材料制成。
根据本发明的一实施例，从y＝D/2-t处的截面线与挤压主体管壁的交点开始至T min所在位置的这一段区域内，挤压主体的壁厚逐渐减小。
根据本发明的一实施例，在y＝D/2-t处的截面线与挤压主体管壁的交点至分流支管上弯曲段延伸末端的这一段区域内，挤压主体的壁厚均大于等于分流支管上弯曲段延伸末端的壁厚。
根据本发明的一实施例，两根分流支管的中心距与分流支管上弯曲段延伸末端的外径之比在2.2～4倍之间。
根据本发明的一实施例，主管接管包括接管直段和接管连接段，接管直段部分或全部内套焊接于挤出主管，接管连接段包括至少一个扩口段、至少一个缩口段或至少一个扩口段和至少一个缩口段的组合。
根据本发明的一实施例，每一分流支管均具有连接段，连接段包括至少一个扩口段、至少一个缩口段或至少一个扩口段和至少一个缩口段的组合。
根据本发明的一实施例，大规格分歧管适用于使用R22、R32、R125、R134A、R410A、R407C这些制冷剂的空调制冷系统。
综上所述，本实施例提供的大规格分歧管在壁厚这一耐压影响因素的基础上引入主管接管插入端端面与挤压主管上T min所在位置的关系这另一因素来实现大规格分歧管耐压性能的双变量调节。主管接管插入端端面位置的调整所带来的产品耐压性能的提升为挤压前原始管 件壁厚的选型提供了更多的空间，从而使得本实施例提供的大规格分歧管在保证产品耐压性能满足标准设计要求的前提下实现了挤压前原始管件壁厚的最优选择，极大地降低了大规格分歧管的成本。
为让本发明的上述和其它目的、特征和优点能更明显易懂，下文特举较佳实施例，并配合附图，作详细说明如下。
附图说明
图1和图2所示为现有大规格分歧管的结构示意图。
图3所示为本发明一实施例提供的大规格分歧管的结构示意图。
图4所示为通过压力测试试验形成数据表1时试验品的结构示意图。
图5所示为图4的局部放大图。
图6所示为图3所示的大规格分歧管在挤压主管附近的局部剖面示意图。
图7所示为图3所示的大规格分歧管的另一局部剖面示意图。
图8所示为图3所示的大规格分歧管中主管接管插入端端面的调整示意图。
图9所示为图3所示的大规格分歧管的加工流程示意图。
具体实施方式
为弥补管体经挤压后一体成型的这类大规格分歧管因挤压摩擦阻力大、材料难以补偿至挤出端而带来的挤出区域耐压性差的问题，当前主要是采用增加原始管材壁厚的方式来加大挤出区域壁厚，进而提升该区域的耐压性。但由于受挤压工艺的影响，原始管材壁厚的增加量和耐压性能之间没有具体的关系，原始管材壁厚的选择是模糊的，设计人员通常只能通过经验给出一个较大的壁厚来满足管件的耐压性要求。然而，对于体积较大的大规格分歧管而言，材料成本对于原始管材壁厚的增加量非常敏感，壁厚的略微增加即有可能导致材料成本的大幅度提升。
有鉴于此，本实施例提供一种大规格分歧管；如图3至图7所示，该大规格分歧管包括挤压主体1和主管接管2。挤压主体1由一根管件经挤压后一体成型，挤压主体1包括挤出主管11和两根分流支管，主管接管2内套焊接于挤出主管11。每一分流支管均具有连通挤 出主管11的弯曲段且弯曲段向远离挤出主管的方向弯曲延伸，弯曲段延伸末端的外径D大于22毫米且两根分流支管中较短那根的长度大于等于挤出主管11长度的3倍。分流支管的长度指的是两根分流支管连通区的中心线和挤出主管轴线的交点至分流支管端面的垂直距离；挤出主管的长度指的是两根分流支管连通区的中心线和挤出主管轴线的交点至挤出主管端面的垂直距离。
具体而言，如图3、图6以及图7所示，两根分流支管分别为第一分流支管12和第二分流支管13。第一分流支管12包括沿其延伸方向依次连接的第一弯曲段121和第一连接段122，第一弯曲段121和挤出主管11之间经第一过渡段141曲面过渡连接；第一弯曲段121的延伸末端指的是第一弯曲段121和第一连接段122连接处的位置，如图3和图7中的P4位置。第二分流支管13包括沿其延伸方向依次连接的第二弯曲段131、第二直段132以及第二连接段133，第二弯曲段131和挤出主管11之间经第二过渡段142曲面过渡连接；第二弯曲段131的延伸末端指的是第二弯曲段131和第二直段132连接处的位置，如图3和图7中的P4’位置。于本实施例中，第一弯曲段121延伸末端和第二弯曲段131延伸末端的外径D大致相等且两者在该处的壁厚t也大致相等。
然而，本发明对第一分流支管12和第二分流支管13的具体结构不作任何限定。于其它实施例中，第一分流支管的结构也可与第二分流支管相同，如包括依次连接的第一弯曲段、第一直段以及第一连接段；此时，第一弯曲段的延伸段末端指的是第一弯曲段和第一直段的连接处。同样的，于其它实施例中，第二分流支管的结构也可只包括第二弯曲段和第二连接段。
为解决管体经挤压后一体成型这类大规格分歧管在挤出主管及其附近区域耐压性薄弱的问题，基于图3和图4所示的大规格分歧管结构，发明人进行了大量的压力测试试验，试验的条件来源于GB4706.32-2012标准所规定的压力测试条件。
制冷剂的选取：选择型号为R410A的制冷剂。
试验品选取：根据分流支管上弯曲段延伸末端的外径D选取十一个试验组，每一试验组内又根据弯曲段延伸末端的壁厚形成三个子试验组。每一子试验组内通过测量主管接管2的 插入端端面在不同位置所对应的挤出主管11的壁厚T1来形成九个试验品。如图4和图5所示，为更好地描述主管接管2的插入端端面与挤出主管11的相对位置关系，试验中以挤出主管11的端面为基准面，通过主管接管2的插入深度H来表征主管接管2插入端端面在挤出主管11上的位置。在试验品选取时，分流支管上弯曲段延伸末端的外径D指的是公称外径。
其中，第一试验组中弯曲段延伸末端的外径D＝25mm；其包含的子试验组中弯曲段延伸末端的壁厚t＝0.85mm,0.95mm,1mm；每一子试验组内主管接管2的插入深度H＝3mm，4mm，5mm，6mm，7mm，8mm，9mm，10mm，11mm。
第二试验组中弯曲段延伸末端的外径D＝28mm；其包含的子试验组中弯曲段延伸末端的壁厚t＝0.9mm,1mm,1.1mm；每一子试验组内主管接管2的插入深度H＝5mm，6mm，7mm，8mm，9mm，10mm，11mm，12mm，13mm。
第三试验组中弯曲段延伸末端的外径D＝31.8mm；其包含的子试验组中弯曲段延伸末端的壁厚t＝1mm,1.1mm,1.2mm；每一子试验组内主管接管2的插入深度H＝5mm，6mm，7mm，8mm，9mm，10mm，11mm，12mm，13mm。
第四试验组中弯曲段延伸末端的外径D＝35mm；其包含的子试验组中弯曲段延伸末端的壁厚t＝1.05mm,1.15mm,1.25mm；每一子试验组内主管接管2的插入深度H＝7mm，8mm，9mm，10mm，11mm，12mm，13mm，14mm，15mm。
第五试验组中弯曲段延伸末端的外径D＝38mm；其包含的子试验组中弯曲段延伸末端的壁厚t＝1.15mm,1.25mm,1.35mm；每一子试验组内主管接管2的插入深度H＝7mm，8mm，9mm，10mm，11mm，12mm，13mm，14mm，15mm。
第六试验组中弯曲段延伸末端的外径D＝42mm；其包含的子试验组中弯曲段延伸末端的壁厚t＝1.25mm,1.35mm,1.45mm；每一子试验组内主管接管2的插入深度H＝7mm，8mm，9mm，10mm，11mm，12mm，13mm，14mm，15mm。
第七试验组中弯曲段延伸末端的外径D＝45mm；其包含的子试验组中弯曲段延伸末端的壁厚t＝1.35mm,1.45mm,1.55mm；每一子试验组内主管接管2的插入深度H＝7mm，8mm，9mm，10mm，11mm，12mm，13mm，14mm，15mm。
第八试验组中弯曲段延伸末端的外径D＝48mm；其包含的子试验组中弯曲段延伸末端的壁厚t＝1.45mm,1.55mm,1.65mm；每一子试验组内主管接管2的插入深度H＝7mm，8mm，9mm，10mm，11mm，12mm，13mm，14mm，15mm。
第九试验组中弯曲段延伸末端的外径D＝50.8mm；其包含的子试验组中弯曲段延伸末端的壁厚t＝1.55mm,1.65mm,1.75mm；每一子试验组内主管接管2的插入深度H＝9mm，10mm，11mm，12mm，13mm，14mm，15mm，16mm，17mm。
第十试验组中弯曲段延伸末端的外径D＝54mm；其包含的子试验组中弯曲段延伸末端的壁厚t＝1.55mm,1.75mm,1.85mm；每一子试验组内主管接管2的插入深度H＝9mm，10mm，11mm，12mm，13mm，14mm，15mm，16mm，17mm。
第十一试验组中弯曲段延伸末端的外径D＝63mm；其包含的子试验组中弯曲段延伸末端的壁厚t＝1.9mm,2.0mm,2.1mm；每一子试验组内主管接管2的插入深度H＝10mm，11mm，12mm，13mm，14mm，15mm，16mm，17mm，18mm。
基于标准GB4706.32-2012所规定压力测试条件对上述297个试验品进行试验，试验数据汇总后如表1所示。分析表1中任一试验组的数据后发现：基于确定的分流支管上弯曲段延伸末端的外径D，大规格分歧管的整体耐压性与主管接管2的插入端端面所在处的挤出主管11的壁厚T1相关。具体而言，当主管接管2的插入端端面所在处的挤出主管的壁厚T1大于某一壁厚临界点T min时大规格分歧管的耐压性能将满足标准GB4706.32-2012所规定的压力测试条件。如第一试验组中的第二子试验组和第三子试验组所示，当主管接管2的插入端端面所在处的壁厚T1大于0.76mm这一临界壁厚T min时大规格分歧管的整体耐压性将满足标准规定。
本实施例提供的大规格分歧管中，挤压主体1是由一根管件挤压成型且挤压主管11为挤出端。挤压工艺中材料的流动补偿决定了：沿主管接管2的插入方向挤出主管11上的壁厚将逐渐增加。因此，在进行主管接管2的焊接装配时只需控制主管接管2的插入端端面所处位置，以使其平齐于或延伸过挤出主管上T min所在的位置即可保证大规格分歧管的整体耐压性能满足标准GB 4706.32-2012所规定的压力试验条件。
由于挤压主管上T min所在处位置是主管接管2焊接时其插入端端面的定位基础，故在大规 格分歧管设计时，对于给定的分流支管上弯曲段延伸末端的外径D首先需要确定挤出主管11上的T min。将表1中每一试验组内挤压主管11的T min进行汇总形成表2，对表2作进一步分析后发现：每一实验组内，挤压主管11上的T min与弯曲段延伸末端的外径D有关且两者呈一定的线性关系。此外，由于挤压主管上T min的确定是基于标准GB4706.32-2012所规定的压力测试条件，而该压力测试条件又与制冷剂的饱和蒸汽压力相关。因此，为进一步研究影响挤压主管上T min的因素，发明人通过更换制冷剂类型来重复上述压力试验并记录不同制冷剂下弯曲段延伸末端的外径D和挤压主管上T min的对应关系，形成表3；选取更换的制冷剂为R22、R32、R125、R134A以及R407C这五种。
表3数据的分析验证：挤压主管11上的T min除了与弯曲段延伸末端的外径D相关外还与每种制冷剂的饱和蒸汽压力相关，基于这一关联关系对表2和表3的数据进行模拟运算后得到如下最小壁厚模型关系：
T min＝KD-b    公式一
其中，T min为大规格分歧管满足标准GB 4706.32-2012所规定的压力测试试验时挤出主管11上的最小壁厚，制冷剂饱和蒸汽压力相关系数K和常数b可通过索引制冷剂饱和蒸汽压力相关系数表(即表4)所得。
公式一和表4的建立使得本实施例提供的大规格分歧管在设计时能基于给定的分流支管上弯曲段延伸末端的外径D和空调系统所使用的制冷剂类型来计算挤出主管11上的T min。为兼顾挤压工艺和测量误差，优选的，在根据公式一和表4计算得到挤出主管11上的T min后可上下浮动3％。
在得到挤出主管的T min后需要在挤出主管上确定T min所对应的位置。于本实施例中，如图6所示，以两根分流支管连通区的中心线和挤出主管11轴线的交点作为坐标系原点O，并以挤出主管11轴线为Y轴，垂直于Y轴的方向为X轴构建直角坐标系。以坐标系原点O为基准对挤压主管11上T min所对应的位置P1和主管接管2的插入端端面所在的位置P2进行描述。具体而言，定义：在Y轴方向上，主管接管2的插入端端面所在的位置P2至坐标原点O的距离为L y；挤出主管上T min所在的位置P1至坐标原点O的距离为L max。由上文分析可知， 为使大规格分歧管的耐压性能满足标准GB 4706.32-2012所规定的压力测试条件，要求主管接管2的插入端端面所在的位置P2要平齐于或延伸过挤压主管11上T min所对应的位置P1；即L y≤L max。空间直角坐标系的建立将主管接管2的插入端端面所在的位置P2和挤压主管11上T min所在位置P1转换为距离的关系。基于图3所示的大规格分歧管的结构和大量挤压样品的测试分析，设置：
L max＝αD-t+n
其中，D为分流支管上弯曲段延伸末端的外径，在图7中为位置P4和P4’处的外径；t为弯曲段延伸末端的壁厚，在图7中为位置P4和P4’处的壁厚；α为一常数且α＝0.56～0.8；n＝0mm～4.5mm。优选的，设置n＝0mm～2.3mm。然而，本发明对此不作任何限定；于其它实施例中，n的上限可以选取0mm～4.5mm内的其它数值。考虑实际加工中挤压主管和分流支管之间的过渡段的曲面半径以及挤压主管内径整圆等工艺的影响，设置α为具有一定修正范围的常数。
基于L max的给定，本实施例提供的大规格分歧管在进行主管接管2焊接时只需控制主管接管2插入端端面所在位置P2至坐标原点O的距离L y≤αD-t+n即可使图3所示的大规格分歧管的整体耐压性满足标准规定。然而，在制冷系统中，制冷剂是沿着管件的内壁快速流动的；当主管接管2的插入端端面伸入到两个分流支管的连通区时，主管接管2的插入端势必会阻碍制冷剂的流通，制冷剂会在主管接管2插入端和连通区内壁所围成的区域内形成涡流，从而影响到空调运行的能效比。有鉴于此，本实施例对L y的下限L min进行限定并设置L min＝D/2-t；结合L max可以得到L y的调整范围：
L y∈[L min,L max]；
即：L y∈[D/2-t,αD-t+n]；
基于公式一所构建的最小壁厚模型和L y的调整范围，在设计本实施例提供的大规格分歧管时，首先根据确定的分流支管上弯曲段延伸末端的外径D和制冷剂类型采用公式一来预测挤压主管11上的T min。之后，根据预测所得到的T min来指导挤压工艺前原始管件壁厚的选型，在保证挤压后挤出主管11上存在T min这一前提下选择经济性最优的原始管件壁厚来进行挤压。 最后，在L min和L max所给定的取值范围内调整主管接管2插入端端面所在位置P2至坐标原点O的距离L y以使本实施例提供的大规格分歧管的产品耐压性满足标准规定；如图8所示，其中虚线表示主管接管2插入端端面延伸至y＝L min这个位置处。图9所示为图3所示的大规格分歧管的加工流程示意图。
于本实施例中，L min和L max可基于分流支管上弯曲段延伸末端的外径D和该处的壁厚t计算后直接确定，产品设计便捷且不受测量误差的影响。然而，本发明对此不作任何限定。于其它实施例中，基于T min选取经济性最优的原始管件壁厚进行挤压形成挤压主体1后，也可通过多次测量挤压样品的方式在挤出主管上标识T min所处的位置。
如图7所示，本实施例提供的大规格分歧管中，从y＝D/2-t处的截面线与挤压主体1管壁的交点P3开始至T min所在的位置P1的这一段区域内，挤压主体1的壁厚逐渐减小。故优选的，在焊接主管接管2时可以使主管接管2插入端端面尽可能靠近P3所在的位置(即使L y尽可能接近L min)以提高大规格分歧管整体的耐压性能。此外，对于主管接管2而言，为保证其与挤出主管11焊接后具有足够的连接强度，装配时还需要考虑两者焊接后的焊接深度。优选的，设置主管接管2与挤出主管11焊接后的焊接深度大于等于弯曲段延伸末端的外径D的0.2倍，所述焊接深度指的是焊缝内焊料熔深的最大深度，如图5和图6中的距离L所示。
如图7所示，本实施例提供的大规格分歧管中，在y＝D/2-t处的截面线与挤压主体管壁的交点P3至第一弯曲段121延伸末端(图7中位置P4处)的这一段区域内挤压主体的壁厚均大于等于第一弯曲段121延伸末端(位置P4处)的壁厚t。同样的，在y＝D/2-t处的截面线与挤压主体管壁的交点P3至第二弯曲段131延伸末端(图7中位置P4’处)的这一段区域内挤压主体的壁厚均大于等于第二弯曲段131延伸末端(位置P4处’)的壁厚t。
于本实施例中，挤压主体1和主管接管2均为铜材料制成且两根分流支管的中心距与分流支管上弯曲段延伸末端的外径D之比在2.2～4倍之间。然而，本发明对此不作任何限定。
于本实施例中，主管接管2包括接管直段21和接管连接段22，接管直段21部分内套焊接于挤出主管11，接管连接段22包括两个外径逐渐变大的扩口段。然而，本发明对此不作 任何限定。于其它实施例中，接管直段也可全部内套于挤出主管；或者，接管连接段也可包括一个或三个以上的扩口段、至少一个缩口段或至少一个扩口段和至少一个缩口段的组合。
同样的，如图3所示，第一分流支管12上的第一连接段122也包括两个外径逐渐变大的扩口段。第二分流支管13上的第二连接段133亦包括两个外径逐渐变大的扩口段。然而，本发明对此不作任何限定。于其它实施例中，第一连接段和第二连接段也可包括一个或三个以上的扩口段、至少一个缩口段或至少一个扩口段和至少一个缩口段的组合。
综上所述，本实施例提供的大规格分歧管在壁厚这一耐压影响因素的基础上引入主管接管插入端端面与挤压主管上T min所在位置的关系这另一因素来实现大规格分歧管耐压性能的双变量调节。主管接管插入端端面位置的调整所带来的产品耐压性能的提升为挤压前原始管件壁厚的选型提供了更多的空间，从而使得本实施例提供的大规格分歧管在保证产品耐压性能满足标准设计要求的前提下实现了挤压前原始管件壁厚的最优选择，极大地降低了大规格分歧管的成本。
虽然本发明已由较佳实施例揭露如上，然而并非用以限定本发明，任何熟知此技艺者，在不脱离本发明的精神和范围内，可作些许的更动与润饰，因此本发明的保护范围当视权利要求书所要求保护的范围为准。
表一
表1中，试验品中弯曲段延伸末端的外径D、弯曲段延伸末端的壁厚t、插入深度H以及挤出主管插入端端面所在处的挤出主管壁厚T1的单位均为mm。
Figure PCTCN2022135398-appb-000001
Figure PCTCN2022135398-appb-000002
Figure PCTCN2022135398-appb-000003
表二
弯曲段延伸末端的外径D(mm) 最小壁厚值Tmin(mm)
25 0.77
28 0.87
31.8 0.98
35 1.08
38 1.18
42 1.3
45 1.39
48 1.48
50.8 1.57
54 1.67
63 1.95
表三
Figure PCTCN2022135398-appb-000004
表四
Figure PCTCN2022135398-appb-000005

Claims (11)

  1. 一种大规格分歧管，其特征在于，包括：
    挤压主体，由一根管件经挤压后一体成型，所述挤压主体包括挤出主管和两根分流支管，每一分流支管均具有连通挤出主管的弯曲段且所述弯曲段向远离挤出主管的方向弯曲延伸，弯曲段延伸末端的外径大于22毫米且两根分流支管的最短长度大于或等于挤出主管长度的3倍；
    主管接管，内套焊接于挤出主管；沿主管接管的插入方向，所述主管接管的插入端端面平齐于或延伸过挤出主管上T min所在的位置，所述T min与分流支管上弯曲段延伸末端的外径D以及制冷剂饱和蒸汽压力相关系数K满足以下最小壁厚模型：
    T min＝KD-b；
    其中，所述T min为大规格分歧管满足GB4706.32-2012标准所规定的压力测试试验时挤出主管上的最小壁厚，制冷剂饱和蒸汽压力相关系数K和常数b通过索引制冷剂的饱和蒸汽压力相关系数表所得。
  2. 根据权利要求1所述的大规格分歧管，其特征在于，以两根分流支管连通区的中心线和挤出主管轴线的交点作为坐标系原点，挤出主管轴线为Y轴，垂直于Y轴的方向为X轴；在Y轴方向上，主管接管插入端端面至坐标原点的距离L y满足以下条件：
    L y∈[L min,L max]；
    L min＝D/2-t；
    L max＝αD-t+n；
    其中，L max指的是：在Y轴方向上，T min所在的位置至坐标原点的距离；D为分流支管上弯曲段延伸末端的外径；t弯曲段延伸末端的壁厚；α为一常数且α＝0.56～0.8；n＝0mm～4.5mm。
  3. 根据权利要求2所述的一种大规格分歧管，其特征在于，主管接管插入端端面至坐标原点的距离L y所需满足的L max中，n＝0mm～2.3mm。
  4. 根据权利要求1所述的一种大规格分歧管，其特征在于，主管接管的焊接深度大于等于分流支管上弯曲段延伸末端外径的0.2倍，所述焊接深度指的是焊缝内焊料熔深的最大深度。
  5. 根据权利要求1所述的一种大规格分歧管，其特征在于，所述挤压主体和主管接管均为铜材料制成。
  6. 根据权利要求2所述的一种大规格分歧管，其特征在于，从y＝D/2-t处的截面线与挤压主体管壁的交点开始至T min所在位置的这一段区域内，挤压主体的壁厚逐渐减小。
  7. 根据权利要求2或6所述的一种大规格分歧管，其特征在于，在y＝D/2-t处的截面线与挤压主体管壁的交点至分流支管上弯曲段延伸末端的这一段区域内挤压主体的壁厚均大于等于分流支管上弯曲段延伸末端的壁厚。
  8. 根据权利要求1所述的一种大规格分歧管，其特征在于，两根分流支管的中心距与分流支管上弯曲段延伸末端的外径之比在2.2～4倍之间。
  9. 根据权利要求1所述的一种大规格分歧管，其特征在于，所述主管接管包括接管直段和接管连接段，所述接管直段部分或全部内套焊接于挤出主管，所述接管连接段包括至少一个扩口段、至少一个缩口段或至少一个扩口段和至少一个缩口段的组合。
  10. 根据权利要求1所述的一种大规格分歧管，其特征在于，每一分流支管均具有连接段，所述连接段包括至少一个扩口段、至少一个缩口段或至少一个扩口段和至少一个缩口段的组合。
  11. 根据权利要求1所述的一种大规格分歧管，其特征在于，所述大规格分歧管适用于使用R22、R32、R125、R134A、R410A、R407C这些制冷剂的空调制冷系统。
PCT/CN2022/135398 2022-10-14 2022-11-30 大规格分歧管 WO2024077737A1 (zh)

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