Collecting pipe structure and refrigeration equipment

Abstract

The utility model discloses a header pipe structure and refrigeration equipment and relates to the technical field of air conditioners, the header pipe structure comprises a main pipe, the main pipe is provided with a first end and a second end which are opposite to each other, the first end of the main pipe is open, the second end of the main pipe is closed, and the main pipe is provided with diversion ports used for being communicated with a plurality of branch pipes respectively. The multiple flow dividing openings are formed in the axis direction of the main pipe at intervals, the inner wall of the main pipe is locally arranged in a protruding mode to form a throttling part, and the throttling part is formed in the position between the two flow dividing openings, so that resistance is increased when refrigerants flow towards the second end of the main pipe; the refrigerant located at the first end, close to the main pipe, of the throttling part can more enter the branch pipes on the side, when the refrigerant flows through the throttling part, due to the fact that the space is narrowed, the flow speed is increased and the pressure is reduced, the flow is reduced, the amount of the refrigerant located at the second end, close to the main pipe, of the throttling part is reduced, the refrigerant is more evenly distributed into all the branch pipes, and therefore the service life of the refrigerant is prolonged. And the performance of the air conditioning system is optimized.

Description

Technical Field

[0001] This utility model relates to the field of air conditioning technology, and in particular to a manifold structure and refrigeration equipment. Background Technology

[0002] In current air conditioning systems, flute tubes are used to distribute two-phase refrigerant to multiple branches. Due to the inertia of refrigerant flow, branches farther from the inlet often receive excessive refrigerant flow.

[0003] To address this issue, some existing methods improve refrigerant distribution by adjusting the diameters of the first and second pipes in the main pipeline—specifically, making the diameter of the second pipe at the far end smaller than that at the near end—to reduce the amount of refrigerant in the far-end branches. However, despite using different diameter first and second pipes and requiring drilling and welding of the first pipe to connect the second pipe, the change in the diameter of the second pipe is not significant, thus failing to completely overcome the effects of refrigerant flow inertia. As a result, the refrigerant in the air conditioning system remains unevenly distributed, leading to low cooling or heating efficiency and overall low energy utilization efficiency. Utility Model Content

[0004] The main purpose of this utility model is to propose a manifold structure and refrigeration equipment, which aims to solve the problem that the existing flute-shaped pipe cannot evenly distribute the refrigerant to the branch pipes, resulting in low refrigeration or heating efficiency.

[0005] To achieve the above objectives, the present invention proposes a manifold structure comprising a main pipe having a first end and a second end opposite to each other. The first end of the main pipe is open, and the second end of the main pipe is closed. The main pipe is provided with a branch port for communicating with multiple branch pipes respectively. The multiple branch ports are spaced apart along the axial direction of the main pipe. The inner wall of the main pipe is partially convex and extends beyond the inner wall surface of other parts of the main pipe to form a throttling section, and the throttling section is formed between two of the branch ports.

[0006] In one embodiment, the throttling portion includes an annular protrusion protruding from the inner wall of the main pipe.

[0007] In one embodiment, the annular protrusion has two annular sides facing a first end and a second end of the main tube, respectively, and the two annular sides extend toward each other in a direction away from the inner wall of the main tube.

[0008] In one embodiment, a portion of the main pipe is recessed so that the inner wall of the main pipe forms the throttling section.

[0009] In one embodiment, multiple throttling sections are provided, and each throttling section is disposed between two adjacent diversion ports;

[0010] The plurality of throttling sections are spaced apart along the length of the main pipe, and the protrusion height H of the plurality of throttling sections increases sequentially from the first end to the second end of the main pipe.

[0011] In one embodiment, the throttling portion includes an annular protrusion protruding from the inner wall of the main pipe;

[0012] The plurality of annular protrusions include a first annular protrusion and a second annular protrusion arranged adjacent to each other, wherein the second annular protrusion is disposed on the side of the first annular protrusion near the second end of the main tube;

[0013] The inner diameter of the first annular protrusion is D1, and the inner diameter of the second annular protrusion is D2, wherein 0.3≤D2 / D1≤0.7.

[0014] In one embodiment, the plurality of annular protrusions includes a first annular protrusion closest to the first end of the main tube;

[0015] The inner diameter of the first annular protrusion is D1, and the inner diameter of the main pipe is D3, wherein 0.3≤D1 / D3≤0.7.

[0016] In one embodiment, the distance between the two diversion ports located on both sides of the throttling section is L, wherein L≥5cm.

[0017] This utility model also provides a refrigeration device, which includes a manifold structure. The manifold structure includes a main pipe with a first end and a second end. The first end of the main pipe is open, and the second end of the main pipe is closed. The main pipe is provided with a branch port for communicating with multiple branch pipes respectively. The multiple branch ports are spaced apart along the length of the main pipe. The inner wall of the main pipe is partially convex and extends beyond the inner wall surface of other parts of the main pipe to form a throttling section. The throttling section is formed between two of the branch ports.

[0018] In one embodiment, the refrigeration equipment includes an air conditioner.

[0019] In the technical solution of this utility model, the refrigerant enters the main pipe from the first end and then enters the multiple branch pipes that are respectively connected to the multiple branch ports through the multiple branch ports. By setting the throttling section between two of the branch ports, the resistance when the refrigerant flows towards the second end of the main pipe is increased. The refrigerant located near the first end of the main pipe at the throttling section can enter more of the branch pipe on that side. When the refrigerant flows through the throttling section, the flow rate increases and the pressure decreases due to the narrowing space. This leads to a reduction in flow rate, which reduces the amount of refrigerant located near the second end of the main pipe at the throttling section. This allows the refrigerant to be distributed more evenly to each branch pipe, thus optimizing the performance of the air conditioning system. Attached Figure Description

[0020] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0021] Figure 1 and Figure 2 This is a schematic diagram of an embodiment of a manifold structure in the related art;

[0022] Figure 3 A schematic diagram of an embodiment of the manifold structure provided by this utility model;

[0023] Figure 4 for Figure 3 A partially enlarged view of an embodiment of the main pipe at point A;

[0024] Figure 5 for Figure 3 A partially enlarged view of another embodiment of the supervisor at point A;

[0025] Figure 6 A partial structural schematic diagram of an embodiment of the refrigeration equipment provided by this utility model.

[0026] Explanation of icon numbers:

[0027] 100', flute-shaped tube; 11', first conduit; 12', second conduit;

[0028] 100. Manifold structure; 1. Main pipe; 101. First end; 102. Second end; a. Branch outlet; 10. Throttling section; 1001. Annular side; 11. Main pipe section; 12. Bend section; 2. Branch pipe;

[0029] 200. Heat exchanger.

[0030] The realization of the purpose, functional features and advantages of this utility model will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0031] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present utility model.

[0032] It should be noted that if the embodiments of this utility model involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0033] Furthermore, if the embodiments of this utility model involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this utility model.

[0034] To ensure that refrigeration and air conditioning systems operate at their most efficient and economical level, refrigerant needs to be properly distributed among multiple evaporators or condensers. This ensures that each heat exchanger receives sufficient refrigerant, thereby maximizing heat exchange area and efficiency. If the refrigerant is not properly distributed, some heat exchangers may experience "flooding" due to excessive refrigerant, resulting in insufficient heat transfer. Conversely, insufficient refrigerant may cause the heat exchangers to be underutilized, affecting overall performance.

[0035] Please see Figure 1When the refrigerant enters the flute tube 100' at a certain speed, it tends to maintain its original direction of motion due to inertia. Therefore, upon encountering the first branch, some refrigerant will continue to travel in a straight line instead of immediately turning to enter the branch port. Thus, as the refrigerant continues to flow forward, more refrigerant may flow to subsequent branch ports, especially the farthest ones.

[0036] In current air conditioning systems, flute-shaped pipes 100' are used to distribute two-phase refrigerant to multiple branches. Due to the inertia of refrigerant flow, the second pipe 12', located farther from the inlet, typically receives excessive refrigerant flow. To address this issue, some existing methods improve the distribution effect by adjusting the diameters of the first pipe 11' and the second pipe 12' on the main pipeline—that is, making the diameter of the distal second pipe 12' smaller than that of the proximal pipe. See also... Figure 2 However, despite using first pipe 11' and second pipe 12' of different diameters, and requiring drilling and welding of the first pipe 11' to connect to the second pipe 12', the change in the diameter of the second pipe 12' was not significant, thus failing to completely overcome the effects of refrigerant flow inertia. As a result, the refrigerant in the air conditioning system still could not be evenly distributed, leading to low cooling or heating efficiency and low overall energy utilization efficiency.

[0037] This utility model proposes a manifold structure 100, which aims to solve the problem that existing flute-shaped pipes cannot evenly distribute refrigerant to the branch pipes, resulting in low cooling or heating efficiency.

[0038] Please see Figure 3 In one embodiment of the present invention, the manifold structure 100 includes a main pipe 1, which has a first end 101 and a second end 102 opposite to each other. The first end 101 of the main pipe 1 is open, and the second end 102 of the main pipe 1 is closed. The main pipe 1 is provided with a branch port a for communicating with a plurality of branch pipes 2 respectively. The plurality of branch ports a are spaced apart along the length direction of the main pipe 1. The inner wall of the main pipe 1 is partially protruding and extends beyond the inner wall surface of other parts of the main pipe 1 to form a throttling section 10. The throttling section 10 is formed at a position between two branch ports a.

[0039] It is understood that the main pipe 1 is the main channel for refrigerant flow, and the main pipe 1 has a first end 101 (open) and a second end 102 (closed). The refrigerant enters from the first end 101, flows in the main pipe 1, and is distributed to each branch pipe 2 through the plurality of branch ports a provided thereon, and each branch pipe 2 is connected to the heat exchanger 200.

[0040] The branch port a is an interface provided on the main pipe 1 and connected to each of the branch pipes 2. The multiple branch ports a are distributed at intervals along the length of the main pipe 1 to distribute the refrigerant into different branches.

[0041] The throttling section 10 is located between the two branch ports a. It is formed by a local protrusion on the inner wall of the main pipe 1, see 4. The protrusion can be a portion of the inner wall of the main pipe 1 where the wall thickness increases, see 5. The protrusion can also be the entire main pipe 1 that contracts inward, where the wall thickness does not change, thus forming a protrusion on the inner wall of the main pipe 1. The local pressure loss at this location can force some of the refrigerant to enter the branch port a near the inlet of the main pipe 1 in advance, instead of continuing to flow along the main pipe.

[0042] In the technical solution of this utility model, refrigerant enters the main pipe 1 from the first end 101 and enters the multiple branch pipes 2 that are respectively connected to the multiple branch ports a through the multiple branch ports a. By setting the throttling section 10 between the two branch ports a, the resistance when the refrigerant flows toward the second end 102 of the main pipe 1 is increased. More refrigerant located near the first end 101 of the main pipe 1 in the throttling section 10 can enter the branch pipe 2 on that side. When the refrigerant flows through the throttling section 10, the flow rate increases and the pressure decreases due to the narrowing space. This leads to a reduction in flow rate, which reduces the amount of refrigerant located near the second end 102 of the main pipe 1 in the throttling section 10. This makes the refrigerant more evenly distributed to each branch pipe 2, thus optimizing the performance of the air conditioning system.

[0043] For further information, please refer to [link / reference]. Figure 3 In this embodiment, the throttling section 10 includes an annular protrusion protruding from the inner wall of the main pipe 1.

[0044] The annular protrusion is a raised structure formed inside the main pipe 1, encircling the entire pipe diameter. The annular protrusion has a uniform effect on all refrigerant passing through this location, ensuring that the refrigerant flow reduction effect is uniform across the entire cross-section, providing a more stable throttling effect in the refrigerant flow, unaffected by refrigerant flow direction shifts or turbulence changes.

[0045] Understandably, the annular protrusion, due to its symmetry, can maintain a relatively stable throttling effect under different operating conditions, and can maintain good diversion performance even if the refrigerant flow conditions change (such as flow rate, pressure, etc.). Furthermore, it is relatively simple to manufacture and easy to process.

[0046] Furthermore, in this embodiment, the annular protrusion has two annular sides 1001 facing the first end 101 and the second end 102 of the main pipe 1, respectively, and the two annular sides 1001 extend toward each other in a direction away from the inner wall of the main pipe 1.

[0047] It is understandable that, as the two annular sides 1001 gradually approach each other in the direction away from the inner wall of the main pipe 1 to form a converging channel, whether the refrigerant flows from the first end 101 to the second end 102 of the main pipe 1, or flows from the branch pipe 2 towards the main pipe 1 and then towards the first end 101 of the main pipe 1, the turbulent components in the refrigerant flow can be reduced, making the flow smoother and preventing uneven distribution of refrigerant between different branches, thereby ensuring that each branch receives a relatively balanced supply of refrigerant.

[0048] The throttling section 10 can be formed by welding or bonding protruding parts to the inner wall of the main pipe 1, by welding pipe sections of different diameters, or by internal expansion or 3D printing.

[0049] For details, please continue reading Figure 3 and Figure 5 In this embodiment, a portion of the main pipe 1 is recessed so that the inner wall of the main pipe 1 forms the throttling section 10.

[0050] The main pipe 1 is partially recessed, meaning it undergoes a pipe-shrinking process, i.e., the pipe diameter is reduced. Specifically, this reduction in diameter can be achieved by locally deforming the pipe through squeezing or rolling.

[0051] By using a tube shrinking method, the inner wall of the main pipe 1 can be formed in a gradually narrowing shape, rather than a sudden change, in order to reduce the impact on fluid flow and the possible eddies. When used in refrigerant pipelines, this helps to optimize refrigerant distribution and improve the system's heat exchange efficiency.

[0052] Compared to welding pipe sections of different diameters, pipe reduction avoids creating weld points between two pipe sections, thus reducing the risk of refrigerant leakage.

[0053] Furthermore, in this embodiment, multiple throttling sections 10 are provided, and each throttling section 10 is provided between two adjacent branch ports a; the multiple throttling sections 10 are spaced apart along the length direction of the main pipe 1, and the protrusion height H of the multiple throttling sections 10 increases sequentially from the first end 101 to the second end 102 of the main pipe 1.

[0054] Understandably, as the refrigerant flows from the first end 101 to the second end 102 of the main pipe 1, it continuously passes through multiple throttling sections 10, with each throttling section 10 providing progressively increasing resistance. Because the protrusion height of each throttling section 10 is different, the throttling section 10 closer to the first end 101 of the main pipe 1 presents less resistance to the refrigerant, allowing more refrigerant to pass through quickly. However, as the refrigerant moves further away from the first end 101, the height of the throttling section 10 increases, requiring the refrigerant to overcome greater resistance to continue its journey. This ensures a more balanced refrigerant supply to both the near-end and far-end branch pipes 2, avoiding the problem of excessive refrigerant at the far end in traditional designs.

[0055] It should also be noted that when the manifold structure 100 is used in the heat exchange system, in the cooling mode, the refrigerant flows from the first end 101 of the main pipe 1, flows toward the second end 102, and flows from each of the branch ports a to each of the branch pipes 2; in the heating mode, the refrigerant flows from each of the branch pipes 2 to the main pipe 1, and flows out toward the opening of the first end 101 of the main pipe 1.

[0056] Thus, in heating mode, the refrigerant flowing through the first throttling section 10 near the second end 102 of the main pipe 1 only gathers the refrigerant from the branch pipe 2 near the second end 102 of the main pipe 1, and the amount of refrigerant is not very large. Therefore, the throttling section 10 can be set at a relatively large height. However, the refrigerant flowing through the second throttling section 10 near the second end 102 of the main pipe 1 gathers more refrigerant from the branch pipe 2, and the amount of refrigerant increases. Therefore, the second throttling section 10 needs to be set at a lower height so that more refrigerant can pass through smoothly.

[0057] Because the greater the height of the throttling section 10, the greater the obstruction to the refrigerant, and the amount of refrigerant that can enter each branch pipe 2 also changes accordingly, the size of the multiple throttling sections 10 needs to be set reasonably in order to truly achieve a uniform distribution of the refrigerant.

[0058] Specifically, in this embodiment, the throttling part 10 includes an annular protrusion protruding from the inner wall of the main pipe 1; the plurality of annular protrusions include a first annular protrusion and a second annular protrusion arranged adjacent to each other, the second annular protrusion being disposed on the side of the first annular protrusion near the second end 102 of the main pipe 1; the inner diameter of the first annular protrusion is D1, the inner diameter of the second annular protrusion is D2, wherein 0.3≤D2 / D1≤0.7.

[0059] If D2 / D1 is set to less than 0.3, the refrigerant flow rate at the near-end branch port a will be too high, while the flow rate at the far-end branch port a will still be insufficient. Furthermore, in heating mode, the refrigerant from each branch converges to the main pipe 1, and when it flows through the throttling section 10, the pressure loss is too high and the pressure is too high, resulting in excessive power consumption and low efficiency of the heat exchange system.

[0060] If D2 / D1 is set to be greater than 0.7, the change in the diameter of the inner wall of the main pipe 1 is not significant, the flow obstruction effect is negligible, and therefore it cannot effectively overcome the influence of the refrigerant flow inertia.

[0061] Of course, when performing pipe shrinkage, the characteristics of the pipe material must be considered to ensure that the integrity and service life of the pipe are not damaged. Excessive shrinkage may cause the pipe wall to become thinner, creating stress concentration points and affecting the strength and durability of the pipe.

[0062] Thus, by setting the ratio of D2 / D1 within a reasonable range, the refrigerant distribution can be effectively improved without causing excessive pressure loss or hindering refrigerant flow, and the safety and lifespan of the manifold structure 100 can also be ensured.

[0063] In one embodiment, the plurality of annular protrusions include a first annular protrusion closest to the first end 101 of the main pipe 1; the inner diameter of the first annular protrusion is D1, and the inner diameter of the main pipe 1 is D3, wherein 0.3≤D1 / D3≤0.7.

[0064] This setting keeps the ratio of D1 / D3 within a reasonable range, which can effectively improve refrigerant distribution without causing excessive pressure loss or hindering refrigerant flow, and also ensures the safety and lifespan of the manifold structure 100.

[0065] Furthermore, in this embodiment, the distance between the two diversion ports a located on both sides of the throttling section 10 is L, wherein L≥5cm.

[0066] Since the refrigerant does not have enough time to disperse and redistribute within a short distance, if the distance between two adjacent branch ports a is too small, the refrigerant's flow inertia and pressure change within such a short distance will be minimal, and the two branch ports a will be allocated almost the same amount of refrigerant. Therefore, there is no need to perform pipe shrinkage treatment at the position between the two branch ports a.

[0067] A larger spacing allows the refrigerant sufficient time and space to disperse naturally, enabling each branch port a to receive the expected amount of refrigerant more accurately. Setting the spacing between two branch ports a to 5 cm or more ensures proper refrigerant distribution at each branch port a, avoiding uneven refrigerant distribution due to excessive proximity.

[0068] Furthermore, in this embodiment, the main pipe 1 includes a main pipe section 11 and a curved pipe section 12 connected to one end of the main pipe section 11. The curved pipe section 12 is folded back from one end of the main pipe section 11 toward the other end. The end of the main pipe section 11 away from the curved pipe section 12 forms the first end 101 of the main pipe 1, and the curved pipe section 12 forms the second end 102 of the main pipe 1.

[0069] When refrigerant flows into the main pipe 1 at a certain speed, it tends to continue flowing in the original direction due to its inertia. If the main pipe 1 is set to a straight line, the refrigerant will more easily rush to the far-end branch port a, resulting in insufficient refrigerant at the near-end branch port a.

[0070] By incorporating a bend or curve before the branch port a, the refrigerant can be forced to change its flow direction, slowing its velocity and reducing the effects of inertia, allowing more refrigerant to enter each branch port a. The curved design provides greater flexibility to adapt to different installation environments and space constraints, while also helping to avoid other pipes or components.

[0071] This utility model also proposes a refrigeration device, which includes a heat exchanger 200 and a manifold structure 100. The specific structure of the manifold structure 100 is as described in the above embodiments. Since this refrigeration device adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0072] The refrigeration equipment can be a refrigerator, an air conditioner, etc. In this embodiment, the refrigeration equipment includes an air conditioner. By setting the manifold structure 100 in the air conditioner, the air conditioner can have a good heating or cooling effect.

[0073] The above description is merely an exemplary embodiment of the present utility model and does not limit the patent scope of the present utility model. Any equivalent structural transformations made based on the technical concept of the present utility model and the contents of the present utility model specification and drawings, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present utility model.

Claims

1. A manifold structure, characterized in that, The device includes a main pipe having a first end and a second end, the first end of which is open and the second end of which is closed. The main pipe is provided with a branch port for communicating with multiple branch pipes respectively. The multiple branch ports are spaced apart along the axis of the main pipe. The inner wall of the main pipe is partially convex and extends beyond the inner wall surface of other parts of the main pipe to form a throttling section, and the throttling section is formed between two of the branch ports.

2. The manifold structure as described in claim 1, characterized in that, The throttling section includes an annular protrusion protruding from the inner wall of the main pipe.

3. The manifold structure as described in claim 2, characterized in that, The annular protrusion has two annular sides facing the first end and the second end of the main tube, respectively, and the two annular sides extend toward each other in a direction away from the inner wall of the main tube.

4. The manifold structure as described in claim 1, characterized in that, The main pipe is partially recessed so that the inner wall of the main pipe forms the throttling section.

5. The manifold structure as described in claim 1, characterized in that, The flow-throttling section is provided in multiple ways, and each flow-throttling section is provided between two adjacent flow-diverting ports; The plurality of throttling sections are spaced apart along the length of the main pipe, and the protrusion height H of the plurality of throttling sections increases sequentially from the first end to the second end of the main pipe.

6. The manifold structure as described in claim 5, characterized in that, The throttling section includes an annular protrusion protruding from the inner wall of the main pipe; The plurality of annular protrusions include a first annular protrusion and a second annular protrusion arranged adjacent to each other, wherein the second annular protrusion is disposed on the side of the first annular protrusion near the second end of the main tube; The inner diameter of the first annular protrusion is D1, and the inner diameter of the second annular protrusion is D2, wherein 0.3≤D2 / D1≤0.

7.

7. The manifold structure as described in claim 6, characterized in that, The plurality of annular protrusions include a first annular protrusion closest to the first end of the main tube; The inner diameter of the first annular protrusion is D1, and the inner diameter of the main pipe is D3, wherein 0.3≤D1 / D3≤0.

7.

8. The manifold structure as described in claim 1, characterized in that, The distance between the two diversion ports located on both sides of the throttling section is L, where L≥5cm.

9. A refrigeration device, characterized in that, Includes the manifold structure as described in any one of claims 1 to 8.

10. The refrigeration equipment as described in claim 9, characterized in that, The refrigeration equipment includes an air conditioner.

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