Pipeline structure for centrifugal pump

Abstract

The pipeline structure comprises a first pipeline and a second pipeline, the first pipeline is used for being connected with the inlet end of the centrifugal pump, the first pipeline comprises a first flexible pipe and a supporting structure, and the first flexible pipe is arranged on the outer wall of the supporting structure in a sleeved mode. The supporting structure extends in the length direction of the first flexible pipe body and is used for supporting the first flexible pipe in the radial direction of the first flexible pipe, the second pipeline is used for being connected with the outlet end of the centrifugal pump and comprises a second flexible pipe body and a restraining structure, and the restraining structure is arranged on the outer wall of the second flexible pipe body in a sleeving mode; and the restraining structure extends in the length direction of the second flexible pipe body and is used for limiting the second flexible pipe in the radial direction of the second flexible pipe, and the technical problem that the stability of a hose structure is poor in the positive and negative pressure environment in a centrifugal pump is solved.

Description

Technical Field

[0001] This utility model relates to the field of pipeline technology, and in particular to a pipeline structure for centrifugal pumps. Background Technology

[0002] Centrifugal pumps, as commonly used liquid transfer equipment, are widely used in fluid systems in chemical, HVAC, fire protection, and environmental protection industries. In practical applications, centrifugal pumps are typically connected to upstream and downstream pipelines via flexible hoses to facilitate the introduction and transfer of liquids. Because the inlet of a centrifugal pump is usually under negative pressure during operation to draw in liquid, while the outlet is under positive pressure to discharge liquid to downstream systems, the flexible hose must withstand the mechanical requirements of both negative and positive pressure conditions during use.

[0003] However, existing conventional hose structures are generally made of flexible materials, which are prone to radial collapse or flattening under negative pressure due to external atmospheric pressure. This causes flow channel contraction, and in severe cases, it can even prevent liquid from being drawn in properly, affecting pump efficiency or causing system failure. At the same time, under the positive pressure at the outlet end, if the hose body lacks sufficient pressure-resistant structure, it is also prone to bulging, swelling, or even bursting, leading to system leakage or safety hazards.

[0004] Currently, the solution to the above problems is mostly to periodically replace the hoses, but this leads to a significant increase in maintenance costs and poor system reliability. Therefore, how to improve the hose structure to adapt to both negative and positive pressure environments has become an urgent technical problem to be solved in this field. Utility Model Content

[0005] One objective of this invention is to provide a pipeline structure for centrifugal pumps, which aims to solve the technical problem of poor stability of hose structures under positive and negative pressure environments in centrifugal pumps.

[0006] To achieve the above objectives, the present invention provides a solution as follows: a pipeline structure for a centrifugal pump, the pipeline structure comprising a first pipeline for connecting to the inlet end of the centrifugal pump, the first pipeline comprising a first flexible tube and a support structure, the first flexible tube being sleeved on the outer wall of the support structure, the support structure extending along the length direction of the first flexible tube, the support structure being used to provide support for the first flexible tube radially; and a second pipeline for connecting to the outlet end of the centrifugal pump, the second pipeline comprising a second flexible tube and a constraint structure, the constraint structure being sleeved on the outer wall of the second flexible tube, the constraint structure extending along the length direction of the second flexible tube, the constraint structure being used to restrict the second flexible tube radially.

[0007] Optionally, the support structure includes at least one first metal wire, which extends along the length of the first flexible tube in a helical trajectory.

[0008] Optionally, the helix angle of the first metal wire is 5° to 20°.

[0009] Optionally, the cross-sectional diameter of the first metal wire is 0.5 mm to 2.5 mm.

[0010] Optionally, the support structure is fixed to the inner wall of the first flexible tube by an adhesive layer.

[0011] Optionally, the constraint structure includes multiple second metal wires, which are woven together to form a cross mesh structure that extends along the length of the second flexible tube.

[0012] Optionally, the weaving density of the cross-grid structure is 5 to 12 meshes.

[0013] Optionally, the cross-sectional diameter of the second metal wire is 1.0 mm to 2.0 mm.

[0014] Optionally, the constraint structure protrudes at both ends of the second flexible tube to form reinforcing rings in the axial direction. The inner diameter of the reinforcing rings is smaller than the outer diameter of the second flexible tube, and the outer diameter of the reinforcing rings is larger than the outer diameter of the second flexible tube.

[0015] Optionally, the width W of the reinforcing ring and the wall thickness T of the second flexible tube body satisfy the following condition: 1.2T≤W≤2T.

[0016] The beneficial effects of this utility model are as follows:

[0017] Compared to existing technologies where flexible hoses may flatten or collapse due to inlet negative pressure, or bulge or rupture due to outlet positive pressure, leading to limited system flow, unstable operation, and frequent hose replacements, this application addresses these issues by introducing a support structure extending along the hose body at the inlet section and a constraint structure conforming to the outer wall of the hose at the outlet section. This achieves differentiated structural reinforcement for both negative and positive pressure conditions. The support structure effectively improves the flexible hose's resistance to deformation under negative pressure suction, maintaining pipeline patency; the constraint structure significantly enhances the hose's resistance to bulging under positive pressure, preventing rupture and failure. Through these optimized designs, this application substantially improves the structural stability and service life of the hose under different operating conditions of the centrifugal pump, reducing maintenance frequency and system costs. Attached Figure Description

[0018] 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.

[0019] Figure 1 This is a schematic diagram of the structure of the first pipeline provided in this embodiment of the utility model;

[0020] Figure 2 This is a schematic diagram of the structure of the second pipeline provided in this embodiment of the utility model;

[0021] Figure 3 This is a schematic diagram of a support structure provided in an embodiment of the present utility model;

[0022] Figure 4 This is a schematic diagram of a constraint structure provided in an embodiment of the present utility model.

[0023] Explanation of icon numbers:

[0024] 10. First pipeline; 11. Support structure; 111. First metal wire; 12. First flexible tube; 20. Second pipeline; 21. Constraint structure; 211. Second metal wire; 212. Reinforcing ring; 22. Second flexible tube. Detailed Implementation

[0025] 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 protection scope of the present utility model.

[0026] It should be noted that all directional indicators (such as up, down, left, right, front, back, etc.) in this utility model embodiment are only used to explain the relative positional relationship and movement of each component in a certain specific posture. If the specific posture changes, the directional indicator will also change accordingly.

[0027] It should also be noted that when a component is referred to as being "fixed to" or "set on" another component, it can be directly on the other component or may be connected to an intermediary component. When a component is referred to as being "connected to" another component, it can be directly connected to the other component or indirectly connected to the other component through an intermediary component.

[0028] Please see Figure 1 and Figure 2 , Figure 1 This is a schematic diagram of the structure of the first pipeline 10 provided in this embodiment of the utility model. Figure 2 This is a schematic diagram of the structure of the second pipeline 20 provided in this embodiment of the utility model.

[0029] This utility model provides a pipeline structure for a centrifugal pump, which optimizes the existing hoses to address the problems of easy flattening and cracking under centrifugal pump operation. The pipeline structure includes a first pipeline 10 and a second pipeline 20, which are used to connect the inlet and outlet ends of the centrifugal pump, respectively, to cope with the different stress environments caused by the negative pressure suction at the inlet and the positive pressure discharge at the outlet during the operation of the centrifugal pump.

[0030] Specifically, the first pipeline 10 includes a first flexible pipe body 12 and a support structure 11 extending along its length. The first flexible pipe body 12 is a traditional flexible hose structure, possessing a certain degree of flexibility and airtightness, capable of adapting to installation displacement and minor vibrations. The support structure 11, disposed on its inner wall, is preferably a metal skeleton or an integrally formed rigid support strip, etc., continuously arranged along the length of the pipe body. Its main function is to provide radial support force for the pipeline under negative pressure conditions, preventing deformation such as flattening or collapse of the pipe body. Compared with the traditional flexible body structure, the support structure 11 can effectively maintain the roundness and inner diameter stability of the channel without affecting the flexible connection.

[0031] The second pipeline 20 is located at the outlet end of the centrifugal pump and is responsible for positive pressure drainage. Its structure includes a second flexible tube 22 and a constraint structure 21 on its outer wall. The second flexible tube 22 is similar to the first flexible tube 12, but because it needs to withstand positive pressure, it is equipped with a constraint structure 21 on its outer side to provide radial restraint. This constraint structure 21 can be in the form of a braided layer, a metal mesh sleeve, or a rigid shell. The constraint structure 21 is fitted to the second flexible tube 22 and extends along its length, preventing the tube from bulging, expanding, or rupturing under the high pressure of the internal liquid, thereby ensuring the safety and stability of the liquid drainage process.

[0032] In this embodiment, starting from the stress characteristics of the hose under different operating conditions of the centrifugal pump, the performance of the hose structure is enhanced by introducing internal support at the inlet section and external constraints at the outlet section. The support structure 11 of the first pipeline 10 significantly improves the flexible hose's resistance to collapse under negative pressure, effectively preventing flow restriction or even liquid inlet failure caused by excessive suction. Meanwhile, the constraint structure 21 of the second pipeline 20 improves the flexible hose's resistance to bulging under positive pressure, reducing the risk of cracking caused by pressure fluctuations or continuous impacts. This structure improves the operational reliability of the centrifugal pump system and overcomes the high maintenance costs and system instability problems caused by frequent hose replacements in existing technologies.

[0033] Please see Figure 3 , Figure 3This is a schematic diagram of a support structure 11 provided in an embodiment of the present invention. In some optimized embodiments, the support structure 11 includes at least one first metal wire 111, which extends and winds along the length of the first flexible tube 12 in a helical trajectory. The first metal wire 111 can be made of stainless steel wire, copper alloy wire, or other metal materials with good bending stiffness and elasticity, and its cross-sectional shape can be circular, elliptical, or rectangular to adapt to different radial support requirements. The helical metal wire can be pre-formed and then embedded in the inner layer of the flexible tube.

[0034] Because the metal wire extends continuously along the length of the tube and maintains a spiral shape, the wire structure can provide uniform and continuous circumferential support in the radial direction when the tube is subjected to negative pressure. Compared to ordinary unsupported hoses, the spiral metal wire forms a stable structure similar to a spring skeleton, which can effectively prevent the tube wall from collapsing inward due to external atmospheric pressure, thereby avoiding the problem of reduced liquid flow or even pipe blockage caused by the reduction of the flow cross-section.

[0035] Meanwhile, the spiral arrangement of the metal wires retains the necessary bendability of the flexible tube, enabling the entire first pipeline 10 to meet the installation and adjustment requirements under complex working conditions while possessing high negative pressure resistance, thus enhancing the adaptability and flexibility of the system's piping layout. Furthermore, the spiral structure has a certain shape recovery capability; when the flexible tube is deformed by temporary external force or suction, it can quickly return to its original shape after the external force is removed, further improving the reversibility of pipeline deformation and its service life.

[0036] Furthermore, in order to optimize the mechanical properties of the support structure 11, in some specific embodiments, the helix angle of the first metal wire 111 is preferably set to 5° to 20°. Here, the helix angle refers to the inclination angle of the metal wire relative to the axis of the tube, that is, the angle formed between the axial and tangential directions of the helical trajectory of the metal wire.

[0037] The selection of the helix angle directly affects the circumferential support strength and axial flexibility of the wire support structure 11 on the tube body. When the helix angle is small (close to 5°), the helix of the wire tends to be tightly wound, and its annular density in the radial direction increases, which can more effectively withstand the radial collapse force from negative pressure conditions and improve the tube body's anti-flattening ability, making it suitable for conditions with strong negative pressure and large suction. When the helix angle is large (close to 20°), the axial coverage pitch of the wire decreases, and the axial flexibility of the tube body is enhanced, which is beneficial for the flexible hose to bend and install, but its circumferential support effect is relatively weakened.

[0038] In this embodiment, the helix angle is set within the range of 5° to 20°, balancing stiffness and flexibility. This effectively suppresses structural deformation of the flexible tube in a negative pressure environment without significantly sacrificing the flexible connection capability. Furthermore, in specific implementations, the helix angle can also be fine-tuned according to factors such as the material properties, thickness, and application scenario of the first flexible tube 12 to further match performance requirements.

[0039] In some embodiments, the strength of the support structure 11 is further adjusted, and the cross-sectional diameter of the first metal wire 111 is preferably set to 0.5 mm to 2.5 mm. This cross-sectional diameter is a key parameter affecting the overall stiffness, compressive strength, and embedding adaptability of the metal wire. By controlling the diameter range of the first metal wire 111, the stability and flexibility of the tube structure can be adjusted to adapt to the negative pressure operation conditions at the inlet of the centrifugal pump.

[0040] When the cross-sectional diameter of the metal wire is less than 0.5 mm, although its flexibility is good, its compressive strength decreases significantly. Under strong negative pressure or large suction fluctuations, the metal wire is prone to buckling or deformation due to insufficient radial stiffness, thus failing to provide effective support for the flexible tube. This can lead to phenomena such as tube collapse, inner wall adhesion, or significant reduction in the flow cross-section during operation, and in severe cases, even cause malfunctions such as fluid flow interruption. In addition, small-diameter metal wires are also more prone to fatigue fracture under long-term vibration or pressure cycling, affecting the overall structural lifespan.

[0041] Conversely, when the cross-sectional diameter of the metal wire is greater than 2.5 mm, although its compressive strength is significantly enhanced, the overall bending stiffness of the flexible tube increases, making it difficult for the hose to adapt to complex pipe routing paths during actual installation. Especially in situations requiring large-angle bending, risks such as assembly difficulties, stress concentration, and even local tearing of the tube may occur.

[0042] In this embodiment, the cross-sectional diameter of the first metal wire 111 is controlled between 0.5 mm and 2.5 mm. While ensuring sufficient radial support force, the flexible tube maintains good bendability, thereby effectively preventing system failure caused by negative pressure flattening or excessive structural rigidity.

[0043] Furthermore, regarding the connection method between the support structure 11 and the first flexible tube 12, in some embodiments, the support structure 11 is fixed to the inner wall of the first flexible tube 12 by an adhesive layer to achieve a stable connection between the two. The support structure 11, as a reinforcing member, extends along the length of the first flexible tube 12, while the adhesive layer is located between the metal wire and the flexible tube, serving multiple functions of fixing, buffering, and sealing.

[0044] In practice, the adhesive layer can be made of an elastic bonding material that is highly compatible with the flexible tube, such as hot melt adhesive, silicone rubber adhesive, or polyurethane structural adhesive. During manufacturing, this adhesive layer is applied to the surface of the metal wire by injection, brushing, or co-extrusion, and then bonded to the inner wall of the first flexible tube 12. After natural curing or heat curing, a stable adhesive interface is formed.

[0045] The advantage of this connection method is that the adhesive layer can tightly connect the support structure 11 to the flexible tube, preventing axial or radial slippage of the support structure 11 within the tube due to vibration or fluid impact during operation, thus ensuring the stability of the support position. Furthermore, the adhesive layer provides stress buffering, preventing wear, crushing, or fatigue cracks caused by local stiffness differences, further extending the service life of the tube.

[0046] For constraint structure 21, please refer to Figure 4 , Figure 4 This is a schematic diagram of a constraint structure 21 provided in an embodiment of the present invention. In some optimized embodiments, the constraint structure 21 includes a plurality of second metal wires 211, which are interwoven and arranged according to a set pattern to form a cross mesh structure. The cross mesh structure is attached to or covers the outer wall of the second flexible tube 22 and extends continuously along the length of the tube to provide effective radial constraint on the flexible tube under positive pressure.

[0047] The second metal wire 211 can be made of stainless steel wire, copper wire, or other metal materials with good tensile strength and fatigue resistance. In the braided structure, each metal wire is interwoven at a certain angle to form a grid-like layer. The intersection points can be reinforced by local hot pressing or adhesive treatment to prevent wire displacement or local loosening.

[0048] This cross-braided structure forms a planar stress distribution network on the pipe surface, effectively suppressing the radial expansion tendency of the outer wall of the second flexible pipe 22 when the fluid pressure at the centrifugal pump outlet increases. Compared with a single-direction annular reinforcement structure, the cross-braided structure has good deformation resistance in multiple directions, and can evenly distribute the internal positive pressure on the pipe to the entire braided layer, thereby preventing bulging, peeling, or bursting caused by local stress concentration.

[0049] Furthermore, since the cross angle and weaving density of the metal wires are adjustable, the structure has high flexibility. The opening size, density distribution or weaving angle of the mesh structure can be optimized according to the application requirements to ensure sufficient constraint strength while taking into account the necessary bending performance of the flexible pipe, and avoid laying difficulties due to excessive reinforcement.

[0050] Furthermore, in some preferred embodiments, the weaving density of the cross-grid structure is preferably set to 5 to 12 meshes. Here, the mesh number in the weaving density represents the number of meshes formed by the interlacing of metal wires per inch of length. The higher the mesh number, the denser the interlacing of metal wires per unit area, and the tighter the resulting constraint structure 21.

[0051] When the weaving density is less than 5 mesh, the metal wires in the cross-grid structure are sparsely arranged, making it difficult to provide sufficient radial restraint force to the second flexible tube 22 under high-pressure conditions. Under the positive pressure at the centrifugal pump outlet, the flexible tube is prone to bulging deformation within the gaps in the grid openings. In severe cases, it may even bulge out locally from the grid, causing expansion and bulging, thus failing to achieve effective anti-expansion protection.

[0052] Conversely, when the braiding density is higher than 12 meshes, the mesh spacing is extremely small, and the second metal wire 211 covers the tube surface more densely, increasing the restraint force. However, this also significantly reduces the overall bendability of the flexible tube. Especially in situations where the pipeline layout is complex or requires sharp bends, excessively high braiding density can cause an increase in bending stiffness, leading to difficulties in installation, high rebound force, and even breakage of the braided layer due to stress concentration.

[0053] Therefore, setting the braiding density of the cross-grid structure in the range of 5 to 12 meshes can provide sufficient radial restraint to suppress the bulging deformation of the flexible tube under high pressure, while maintaining the necessary flexibility and bending adaptability to meet the requirements of hose layout in actual engineering.

[0054] In some embodiments, the cross-sectional diameter of the second metal wire 211 is preferably set to 1.0 mm to 2.0 mm. Compared to the first metal wire 111 disposed in the first conduit 10, whose diameter ranges from 0.5 mm to 2.5 mm, the diameter range of the second metal wire 211 is generally narrower, with a higher lower limit and a lower upper limit. This is determined by the difference in the structural functions it undertakes. The first metal wire 111 is mainly used to resist the flattening caused by negative pressure, and its key indicators are anti-collapse stiffness and helical elasticity, and it can accept larger cross-sectional changes. The second metal wire 211 is mainly used to provide full-coverage radial constraint under positive pressure, constructing a shape-stabilizing force shell, and places more emphasis on the continuity, consistency and multi-directional tension synergy of the mesh layer. Therefore, it needs a more uniform and moderately stiff diameter specification to control the overall mesh density and deformation consistency.

[0055] When the diameter of the second metal wire 211 is less than 1.0 mm, its tensile and deformation resistance decreases significantly, easily leading to the failure of the cross-grid structure. Consequently, it cannot apply sufficient constraint force to the second flexible tube 22, resulting in the risk of bulging, swelling, or even rupture. Conversely, if the diameter of the second metal wire 211 is greater than 2.0 mm, its rigidity increases, causing a decrease in the overall flexibility of the cross-braided structure. This can easily lead to localized stress concentration or indentation, affecting the bendability of the second flexible tube 22 and increasing the difficulty of installation. In this embodiment, the cross-sectional diameter of the second metal wire 211 is controlled within the range of 1.0 mm to 2.0 mm, ensuring that the cross-grid structure has sufficient constraint strength while retaining good flexibility.

[0056] In some embodiments, the constraint structure 21 forms annular protrusions at both axial ends of the second flexible tube 22, namely, reinforcing ring 212 structures. The inner diameter of the reinforcing ring 212 is smaller than the outer diameter of the second flexible tube 22, while its outer diameter is larger than the outer diameter of the second flexible tube 22. In other words, the reinforcing ring 212 is structurally constricted inward and expanded outward, forming a pair of protruding annular reinforcing regions relative to the middle section of the constraint structure 21.

[0057] The reinforcing ring 212 can be formed from cross-grid metal wires through methods such as dense weaving, localized thickening by winding, or secondary adhesive coating. To achieve a secure structure, the inner diameter of the reinforcing ring 212 is smaller than the outer diameter of the second flexible tube 22, which can, to a certain extent, create an axial compression fit on the outer wall of the flexible tube, thereby enhancing the stability of the braided structure at the end of the tube and preventing the grid structure from sliding, displacing, or detaching axially under conditions such as high-frequency vibration, thermal expansion and contraction, or positive pressure pulsation. Simultaneously, the outer diameter of the reinforcing ring 212 is larger than the outer diameter of the tube body, and in actual installation, it can serve as an external clamping and positioning point, forming a mechanical limiting fit with pipe joints, locking structures, or flange connections.

[0058] In this embodiment, by providing reinforcing rings 212 at both ends of the constraint structure 21, the axial locking force between the metal braided mesh structure and the second flexible tube 22 is improved, thus preventing structural displacement or failure under positive pressure.

[0059] Furthermore, in some preferred embodiments, the width W of the reinforcing ring 212 and the wall thickness T of the second flexible tube 22 satisfy the following relationship: 1.2T≤W≤2T. Wherein, the width W refers to the axial extension dimension of the reinforcing ring 212, and the wall thickness T is the radial thickness of the second flexible tube 22.

[0060] When the width of the reinforcing ring 212 is less than 1.2T, the axial extension of the reinforcing ring 212 is insufficient, making it difficult to form an effective circumferential support area in practical applications. At this time, the reinforcing ring 212 is prone to stress concentration, edge shearing, and even wire warping or detachment when clamped or locked, making it unable to achieve stable anchoring of the cross-grid structure, and also difficult to continuously play an anti-detachment role under positive pressure impact or pipeline vibration.

[0061] Conversely, if the width of the reinforcing ring 212 is greater than 2T, although its performance in terms of rigidity and resistance to displacement is enhanced, it will cause a sudden change in axial stiffness at the end of the pipe body, affecting the flexibility of the flexible pipe in the connection area. At the same time, it will also increase the length of the rigid-flexible transition zone of the entire pipe body, reducing the overall adaptability of the structure.

[0062] In this embodiment, the width W of the reinforcing ring 212 is designed to be between 1.2 and 2 times the wall thickness T of the flexible tube. Within this range, the reinforcing ring 212 can form a sufficient structural anchoring area, enhancing the axial restraint and anti-slip capability of the cross-grid layer at the ends, ensuring that the tube maintains connection stability under high pressure fluctuations or dynamic fatigue environments. Simultaneously, this range also ensures that the stiffness gradient of the reinforcing ring 212 itself is gradual in the axial direction, without significantly interfering with the flexibility of the tube.

[0063] Furthermore, the use of terms such as "first" and "second" in this utility model is 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 as "first" or "second" may explicitly or implicitly include at least one of that feature. Additionally, the technical solutions of the various embodiments can be combined with each other, but only on the basis of being achievable by those skilled in the art. When the combination of technical solutions is contradictory or impossible to implement, such a combination of technical solutions should be considered non-existent and not within the scope of protection claimed by this utility model.

[0064] The above description is only a preferred embodiment of the present utility model and does not limit the patent scope of the present utility model. All equivalent structural transformations made under the inventive concept of the present utility model using 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 piping structure for a centrifugal pump, the centrifugal pump having an inlet end and an outlet end, characterized in that, include: A first pipeline is used to connect to the inlet end of the centrifugal pump. The first pipeline includes a first flexible pipe and a support structure. The first flexible pipe is sleeved on the outer wall of the support structure. The support structure extends along the length of the first flexible pipe and is used to provide support for the first flexible pipe in the radial direction. The second pipeline is used to connect to the outlet end of the centrifugal pump. The second pipeline includes a second flexible tube body and a constraint structure. The constraint structure is sleeved on the outer wall of the second flexible tube body and extends along the length direction of the second flexible tube body. The constraint structure is used to restrict the second flexible tube body radially.

2. The pipeline structure for a centrifugal pump according to claim 1, characterized in that, The support structure includes at least one first metal wire, which extends along the length of the first flexible tube in a spiral trajectory.

3. The piping structure for a centrifugal pump according to claim 2, characterized in that, The helix angle of the first metal wire is 5° to 20°.

4. The pipeline structure for a centrifugal pump according to claim 2, characterized in that, The cross-sectional diameter of the first metal wire is 0.5 mm to 2.5 mm.

5. The piping structure for a centrifugal pump according to any one of claims 1 to 4, characterized in that, The support structure is fixed to the inner wall of the first flexible tube by an adhesive layer.

6. The piping structure for a centrifugal pump according to claim 1, characterized in that, The constraint structure includes a plurality of second metal wires, which are woven together to form a cross mesh structure that extends along the length of the second flexible tube.

7. The piping structure for a centrifugal pump according to claim 6, characterized in that, The weaving density of the cross-grid structure is 5 to 12 meshes.

8. The piping structure for a centrifugal pump according to claim 6, characterized in that, The cross-sectional diameter of the second metal wire is 1.0 mm to 2.0 mm.

9. The piping structure for a centrifugal pump according to any one of claims 6 to 8, characterized in that, The constraint structure protrudes at both ends of the second flexible tube in the axial direction to form reinforcing rings. The inner diameter of the reinforcing ring is smaller than the outer diameter of the second flexible tube, and the outer diameter of the reinforcing ring is larger than the outer diameter of the second flexible tube.

10. The piping structure for a centrifugal pump according to claim 9, characterized in that, The width W of the reinforcing ring and the wall thickness T of the second flexible tube satisfy the following condition: 1.2T≤W≤2T.

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