A spiral plate heat exchanger suitable for high-pressure fluid heat exchange

Abstract

The application provides a spiral plate heat exchanger suitable for high-pressure fluid heat exchange, which comprises a spiral body and an external connecting pipe, and the spiral body comprises spiral plates, a center partition plate, an upper sealing plate, a lower sealing plate and an end sealing plate. The end sealing plate is curved into an arc-shaped section in the axial direction of the spiral body, one end of the arc-shaped section is connected with the upper sealing plate or the lower sealing plate, and the other end extends towards the external connecting pipe. In the circumferential direction of the spiral body, the width of the arc-shaped section gradually increases, the height of the outermost flow channel in the axial direction of the spiral body gradually decreases, and the width of the outermost flow channel in the radial direction of the spiral body gradually increases. The arc-shaped section can reduce or even eliminate the dead angle of material accumulation, improve the cleanliness, gradually change the flow direction of the material through the arc-shaped section and unload the force, thereby reducing the erosion of the inner wall surface of the outermost flow channel and the impact on the end sealing plate, greatly prolonging the service life and improving the pressure-bearing capacity, and being suitable for the heat exchange of high-pressure fluid with a pressure of 1.6 MPa.

Description

Technical Field

[0001] This invention relates to the field of spiral plate heat exchanger technology, and more specifically to a spiral plate heat exchanger suitable for high-pressure fluid heat exchange. Background Technology

[0002] Spiral plate heat exchangers are a common type of heat exchange equipment, generally consisting of four parts: a shell, a spiral body, a seal, and two sets of inlet and outlet. The spiral body, which serves as the heat transfer element, is made from two parallel steel plates on a special winding bed. Each steel plate is simultaneously wound into a spiral shape, forming two concentric channels. Each channel is a single annular channel with uniform curvature. The outermost part of the channel is connected to a pipe. For example, Chinese patents CN2371531 Y and CN201364057Y disclose this type of spiral plate heat exchanger. Due to the larger cavity formed by the annular channel, it has stronger anti-clogging ability compared to shell-and-tube heat exchangers and lower requirements for the cleanliness of materials passing through the heat exchanger. Therefore, it is widely used in food processing and other fields.

[0003] However, because the diameter of the inlet pipe is much smaller than the vertical height of the channel, only a very small portion of the material in the channel can enter the inlet pipe smoothly and in a timely manner. Dead material corners exist at the connection between the inlet pipe and the channel, easily leading to sludge buildup and poor cleanliness. Furthermore, the end plates at the ends of the channel are elongated and perpendicular to the material flow direction. During use, the flowing material impacts the end plates and drastically changes its flow direction, causing significant scouring of the inner wall of the channel end and easily leading to leaks at the welded joints. This results in a short service life for this type of spiral plate heat exchanger (generally less than 30,000 hours). More importantly, the design of the end plates perpendicular to the material flow direction prevents them from absorbing stress, leaving them to bear the full impact force of the material for extended periods. The supporting force of the end plates is only provided by the surrounding welded points, resulting in poor pressure resistance (typically below 0.6 MPa) for this type of spiral plate heat exchanger, making it unsuitable for heat exchange of high-pressure fluids. Summary of the Invention

[0004] The purpose of this invention is to overcome one or more disadvantages of the prior art and provide a spiral plate heat exchanger suitable for high-pressure fluid heat exchange.

[0005] To achieve the above objectives, the present invention provides a spiral plate heat exchanger suitable for high-pressure fluid heat exchange, comprising:

[0006] A spiral body includes a spiral plate, a central partition, an upper sealing plate, a lower sealing plate, and an end sealing plate. The spiral plate consists of two spiral plates rolled parallel to each other with the central partition as the center. The outer ends of the two spiral plates are located on both sides of the axis of the spiral body. The upper sealing plate and the lower sealing plate are connected to the upper and lower ends of adjacent spiral plates. The end sealing plate is connected between the outer end of one spiral plate and the outer wall of the other spiral plate, so that a flow channel is formed between adjacent spiral plates.

[0007] An outer tube is connected to the spiral body and communicates with the flow channel; the outer tube is located near the outer end of the spiral plate.

[0008] The end cap has an arc-shaped segment that bends into an arc shape in the axial direction of the spiral body. One end of the arc-shaped segment is connected to the upper cap or the lower cap, and the other end extends toward the outer pipe. In the circumferential direction of the spiral body, the width of the arc-shaped segment gradually increases, so that the height of the outermost flow channel in the axial direction of the spiral body gradually decreases while the width in the radial direction of the spiral body gradually increases.

[0009] Preferably, the cross-sectional area of ​​the outermost flow channel is equal at any position in the arc segment.

[0010] Preferably, the angle of the arc segment in the circumferential direction of the helical body is 90° to 180°.

[0011] Preferably, the end cap is formed by connecting the arc-shaped segment and the straight segment, and the extension direction of the straight segment is parallel to the axial direction of the spiral.

[0012] More preferably, the extension length of the straight section is 10%-15% of the height of the helix.

[0013] Preferably, the outer ends of the two spiral plates are symmetrically distributed on both sides of the spiral axis.

[0014] Preferably, the centerline of the outer tube is parallel to the centerline of the spiral body, and the opening of the outer tube away from the flow channel faces upward.

[0015] Preferably, the spiral plate heat exchanger suitable for high-pressure fluid heat exchange further includes a casing, which is coaxially disposed on the outside of the spiral body. The upper edge of the casing is not lower than the upper end face of the spiral body, and the lower edge of the casing is not higher than the lower end face of the spiral body. A cavity is formed between the inner wall of the casing and the outer wall of the spiral body, and the cavity is filled with a heat insulation layer.

[0016] More preferably, a medium tube corresponding to the outermost flow channel is inserted into the insulation layer outside the outermost flow channel. There are multiple medium tubes and they are spaced apart. Cooling medium or heating medium flows through the medium tubes so that the insulation effect is the same at any position of the outermost flow channel.

[0017] More preferably, the upper edge of the enclosure is connected to an upper cover that is higher than the upper end face of the spiral, and the lower edge of the enclosure is connected to a lower cover that is lower than the lower end face of the spiral, so as to form a sealed body. The heat insulation layer is also provided between the upper cover and the upper end face of the spiral, and between the lower cover and the lower end face of the spiral.

[0018] Due to the application of the above technical solution, the present invention has the following advantages compared with the prior art:

[0019] 1. Because the end sealing plate has an arc-shaped section that bends into an arc shape in the axial direction of the spiral body, and one end of the arc-shaped section is connected to the upper or lower sealing plate, while the other end extends towards the outer pipe, the arc-shaped section can reduce or even eliminate the dead corner of sludge and improve cleanliness. It can also gradually change the flow direction of the material through the arc-shaped section, thereby reducing the scouring of the inner wall of the outermost flow channel. This allows the spiral plate heat exchanger to reach or even exceed 100,000 hours in its entire life cycle, greatly extending its service life.

[0020] 2. As the width of the arc segment gradually increases in the circumferential direction of the spiral, the height of the outermost flow channel in the axial direction of the spiral gradually decreases while the width in the radial direction of the spiral gradually increases. This can also relieve pressure while changing the material flow direction, reduce the impact on the end sealing plate, and greatly improve the pressure-bearing capacity of the spiral plate heat exchanger. This makes the spiral plate heat exchanger suitable for heat exchange of high-pressure fluids with pressures up to 1.6 MPa. Attached Figure Description

[0021] Figure 1 This is a front view schematic diagram of Embodiment 1 of the present invention, with a partial cross-sectional view.

[0022] Figure 2 yes Figure 1 A top-view diagram, with a partial cross-section.

[0023] Figure 3 This is a front view schematic diagram of Embodiment 2 of the present invention, with a partial cross-sectional view.

[0024] Figure 4 yes Figure 3 A top-view diagram, with a partial cross-section.

[0025] Figure 5 This is a front view schematic diagram of Embodiment 3 of the present invention, with a partial cross-sectional view.

[0026] Figure 6 yes Figure 5 A top-view diagram, with a partial cross-section.

[0027] Wherein: 10. Spiral body; 11a. First spiral plate; 11b. Second spiral plate; 12. Central partition; 13. Upper sealing plate; 14. Lower sealing plate; 15. End sealing plate; 151. Arc-shaped section; 152. Straight section; 16. Central sealing plate; 17. Flow channel; 21. Outer pipe; 22. Inner pipe; 31. Lifting lug; 32. Support leg; 41. Enclosure; 411. Upper cover; 412. Lower cover; 413. Upper nozzle; 414. Lower nozzle; 42. Cavity; 43. Insulation layer; 44. Medium pipe. Detailed Implementation

[0028] The up and down direction described in this invention refers to Figure 1 , 3 In the vertical direction of 5, in this invention, the side closer to the axis of the spiral is called "inner", and the side farther away from the axis of the spiral is called "outer".

[0029] Example 1

[0030] like Figure 1 and Figure 2As shown, the spiral plate heat exchanger for high-pressure fluid heat exchange provided by the present invention includes: a spiral body 10 and a connecting pipe; wherein, the spiral body 10 includes spiral plates, a central partition plate 12, an upper sealing plate 13, a lower sealing plate 14, an end sealing plate 15, and a central sealing plate 16. There are two spiral plates, namely a first spiral plate 11a and a second spiral plate 11b. These two spiral plates are rolled parallel to each other from the inside out with the central partition plate 12 as the center. The outer ends of these two spiral plates are located on both sides of the axis of the spiral body 10. The upper sealing plate 13 and the lower sealing plate 14 are spiral strips. The upper sealing plate 13 is sealed to the upper end of the adjacent spiral plate, and the lower sealing plate 14 is sealed to the lower end of the adjacent spiral plate. The inner ends of the upper sealing plate 13 and the lower sealing plate 14 are respectively sealed to the upper and lower ends of the central partition plate 12. There are two end sealing plates 15, one of which is connected between the outer end of the first spiral plate 10a and the outer wall of the second spiral plate 10b, and the other is connected between the outer end of the second spiral plate 10b and the outer wall of the first spiral plate 10a. The upper and lower ends of the end sealing plates 15 are respectively sealed to the outer ends of the upper sealing plate 13 and the lower sealing plate 14, so that two independent spiral flow channels 17 are formed between adjacent spiral plates. These two flow channels 17 are used for the flow of materials and heat exchange fluids, respectively. The central sealing plate 16 is sealed to the upper and lower ends of the central partition plate 12. The outer end face of the sealing plate 16 is sealed to the inner wall of the first spiral plate 11a facing the central partition 12 and the inner wall of the second spiral plate 10b facing the central partition 12. The connecting pipe includes an outer connecting pipe 21 and an inner connecting pipe 22, with two outer connecting pipes 21 and two inner connecting pipes 22. The two outer connecting pipes 21 are connected to the spiral body 10 and are respectively connected to two flow channels 17. The two outer connecting pipes 21 are located near the outer end of the spiral plate, and the axis of the two outer connecting pipes 21 is parallel to the axis of the spiral body 10. The openings of the two outer connecting pipes 21 away from the flow channels 17 face the same direction (both upward). The two inner connecting pipes 22 are respectively connected to two passages opened on the lower central sealing plate 16. On the hole, the two inner tubes 22 are located on both sides of the central partition 12. The two inner tubes 22 extend downward for a certain distance and then extend horizontally outward. The openings of the two inner tubes 22 away from the central sealing plate 16 face opposite directions. The end sealing plate 15 has an arc-shaped segment 151 that is bent into an arc shape in the axial (up and down) direction of the spiral body 10. The lower end of the arc-shaped segment 151 is connected to the outer end of the lower sealing plate 14, and the upper end extends towards the outer tube 21. In the circumferential direction of the spiral body 10, the width of the arc-shaped segment 151 gradually increases, so that the height of the outermost flow channel 17 in the axial direction of the spiral body 10 gradually decreases while the width in the radial direction of the spiral body 10 gradually increases.

[0031] The advantage of this setting is that:

[0032] 1. The spiral plate heat exchanger can reduce or even eliminate dead corners of sludge by using the arc section to improve cleanliness. It can also gradually change the flow direction of materials through the arc section, thereby reducing the scouring of the inner wall of the outermost flow channel. This allows the entire life cycle of the spiral plate heat exchanger to reach or even exceed 100,000 hours, greatly extending its service life.

[0033] 2. It can also relieve pressure while changing the direction of material flow, reducing the impact on the end sealing plate and greatly improving the pressure bearing capacity of the spiral plate heat exchanger, making it suitable for heat exchange of high-pressure fluids with pressure up to 1.6MPa.

[0034] To ensure stable flow of materials and heat exchange fluids and avoid excessive changes in their flow velocity, in this embodiment, the cross-sectional area of ​​the outermost flow channel 17 is equal at any position of the arc segment 151.

[0035] To make the most of the heat exchange surface and avoid the arc segment 151 from being too steep, the outer ends of the first spiral plate 10a and the second spiral plate 10b are symmetrically distributed on both sides of the axis of the spiral body 10. The angle of the arc segment 151 in the circumferential direction of the spiral body 10 is 90° to 180° (inclusive). In this embodiment, the angle of the arc segment 151 in the circumferential direction of the spiral body 10 is 90°.

[0036] To facilitate the introduction of materials or heat exchange fluids into the external pipe 21, in this embodiment, the end sealing plate 15 further includes a straight section 152. The end sealing plate 15 is formed by connecting the arc-shaped section 151 and the straight section 152. The straight section 152 is connected to the upper end of the arc-shaped section 151, and the extension direction of the straight section 152 is parallel to the axial direction (vertical direction) of the spiral body 10.

[0037] To ensure the import effect and minimize the length of the straight section 152, the extension length of the straight section 152 is preferably 10%-15% of the height of the spiral 10. In this embodiment, the height of the spiral 10 is 1200mm, the extension length of the straight section 152 is 150mm, and the extension length of the straight section 152 is preferably 12.5% ​​of the height of the spiral 10.

[0038] In this embodiment, the spiral plate heat exchanger also includes lugs 31 and legs 32. There are two lugs 31, which are connected to the outer side of the spiral body 10 and extend vertically upward. The two lugs 31 are symmetrically distributed along the axis of the spiral body 10. The legs 32 are connected to the bottom of the spiral body 10 for support. There are four legs 32, which are evenly distributed around the axis of the spiral body 10.

[0039] Example 2

[0040] like Figure 3 and Figure 4As shown, Embodiment 2 is basically the same as Embodiment 1, except that in Embodiment 2, the spiral plate heat exchanger also includes a cylindrical casing 41. The casing 41 is coaxially covered on the outside of the spiral body 10. The upper edge of the casing 41 is higher than the upper end face of the spiral body 10, and the lower edge of the casing 41 is lower than the lower end face of the spiral body 10. A cavity 42 is formed between the inner wall of the casing 41 and the outer wall of the spiral body 10, and the cavity 42 is filled with a heat insulation layer 43.

[0041] The advantage of this design is that it optimizes the irregular outer wall surface of the spiral, improving the safety, aesthetics, and premium feel of the spiral plate heat exchanger. It also reduces the heat exchange between the outer wall surface of the spiral and the outside environment, minimizing the impact of the ambient temperature on the heat exchange of the spiral plate heat exchanger, and also reducing the impact of the spiral plate heat exchanger on the ambient temperature.

[0042] To further reduce heat exchange between the spiral 10 and the outside environment, in this embodiment, the upper edge of the casing 41 is sealed with an upper cover 411 that is higher than the upper end face of the spiral 10, and the lower edge of the casing 41 is sealed with a lower cover 412 that is lower than the lower end face of the spiral 10, so as to form a sealed body. The upper cover 411 is lower than the upper end face of the lifting lug 31 and the opening of the outer pipe 21, and the lower cover 412 is higher than the lower end face of the support leg 32 and the opening of the inner pipe 22. A heat insulation layer 43 is also provided between the upper cover 411 and the upper end face of the spiral 10, and between the lower cover 412 and the lower end face of the spiral 10.

[0043] Furthermore, the insulation layer 43 is formed by the expansion and hardening of foam sealant. To facilitate the spraying of foam sealant, the upper cover 411 and the lower cover 412 are respectively provided with an upper spray pipe 413 and a lower spray pipe 414 that are connected to the cavity 42.

[0044] Example 3

[0045] like Figure 5 and Figure 6 As shown, Embodiment 3 is basically the same as Embodiment 2, except that in Embodiment 3, a medium pipe 44 corresponding to (with corresponding length) the outermost flow channel 17 is inserted in the insulation layer 43 outside the outermost flow channel 17. There are multiple medium pipes 44 and they are spaced apart. Cooling medium or heating medium is passed through the medium pipes 44 so that the insulation effect is the same at any position of the outermost flow channel 17, thereby reducing the temperature fluctuation of the material and heat exchange fluid, avoiding the change in flow rate caused by volume change, and minimizing the impact of the outer wall shape of the spiral 10 on the scouring effect and pressure bearing capacity.

[0046] It should be noted that the above embodiments also include components such as spacer columns and support rings, which can be set up in accordance with conventional methods.

[0047] The above embodiments are only for illustrating the technical concept and features of the present invention. Their purpose is to enable those skilled in the art to understand the content of the present invention and implement it accordingly. They should not be used to limit the scope of protection of the present invention. All equivalent changes or modifications made in accordance with the spirit and essence of the present invention should be covered within the scope of protection of the present invention.

Claims

1. A spiral plate heat exchanger suitable for high-pressure fluid heat exchange, comprising: A spiral body includes a spiral plate, a central partition, an upper sealing plate, a lower sealing plate, and an end sealing plate. The spiral plate consists of two spiral plates rolled parallel to each other with the central partition as the center. The outer ends of the two spiral plates are located on both sides of the axis of the spiral body. The upper sealing plate and the lower sealing plate are connected to the upper and lower ends of adjacent spiral plates. The end sealing plate is connected between the outer end of one spiral plate and the outer wall of the other spiral plate, so that a flow channel is formed between adjacent spiral plates. An outer tube is connected to the spiral body and communicates with the flow channel; the outer tube is located near the outer end of the spiral plate. Its features are: The end cap has an arc-shaped segment that bends into an arc shape in the axial direction of the spiral body. One end of the arc-shaped segment is connected to the upper cap or the lower cap, and the other end extends toward the outer pipe. In the circumferential direction of the spiral body, the width of the arc-shaped segment gradually increases, so that the height of the outermost flow channel in the axial direction of the spiral body gradually decreases while the width in the radial direction of the spiral body gradually increases.

2. The spiral plate heat exchanger suitable for high-pressure fluid heat exchange according to claim 1, characterized in that: The cross-sectional area of ​​the outermost flow channel is equal at any position in the arc segment.

3. The spiral plate heat exchanger suitable for high-pressure fluid heat exchange according to claim 1, characterized in that: The angle of the arc segment in the circumferential direction of the spiral is 90° to 180°.

4. The spiral plate heat exchanger suitable for high-pressure fluid heat exchange according to claim 1, characterized in that: The end cap is formed by connecting the arc-shaped segment and the straight segment, with the straight segment extending in a direction parallel to the axial direction of the spiral.

5. The spiral plate heat exchanger suitable for high-pressure fluid heat exchange according to claim 4, characterized in that: The extension length of the straight section is 10%-15% of the height of the helix.

6. The spiral plate heat exchanger suitable for high-pressure fluid heat exchange according to claim 1, characterized in that: The outer ends of the two spiral plates are symmetrically distributed on both sides of the spiral axis.

7. The spiral plate heat exchanger suitable for high-pressure fluid heat exchange according to claim 1, characterized in that: The centerline of the outer tube is parallel to the centerline of the spiral body, and the opening of the outer tube facing upwards away from the flow channel.

8. The spiral plate heat exchanger suitable for high-pressure fluid heat exchange according to claim 1, characterized in that: The spiral plate heat exchanger suitable for high-pressure fluid heat exchange also includes a casing, which is coaxially covered on the outside of the spiral body. The upper edge of the casing is not lower than the upper end face of the spiral body, and the lower edge of the casing is not higher than the lower end face of the spiral body. A cavity is formed between the inner wall of the casing and the outer wall of the spiral body, and the cavity is filled with a heat insulation layer.

9. The spiral plate heat exchanger suitable for high-pressure fluid heat exchange according to claim 8, characterized in that: A medium tube corresponding to the outermost flow channel is inserted into the insulation layer located outside the outermost flow channel. There are multiple medium tubes and they are spaced apart. Cooling medium or heating medium flows through the medium tubes so that the insulation effect is the same at any position of the outermost flow channel.

10. The spiral plate heat exchanger suitable for high-pressure fluid heat exchange according to claim 8, characterized in that: The upper edge of the enclosure is connected to an upper cover that is higher than the upper end face of the spiral body, and the lower edge of the enclosure is connected to a lower cover that is lower than the lower end face of the spiral body, so as to form a sealed body. The heat insulation layer is also provided between the upper cover and the upper end face of the spiral body, and between the lower cover and the lower end face of the spiral body.

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