CN118463669A - Spiral plate heat exchanger and heat exchange device for large flow and high viscosity fluid - Google Patents

Abstract

The invention relates to the technical field of heat exchangers, and provides a spiral plate type heat exchanger and a heat exchange device for high-flow high-viscosity fluid, which comprise a shell, wherein a first flow passage and a second flow passage which are not communicated with each other and are in spiral shape are arranged in the shell, corrugated structures are arranged on the wall surfaces of the first flow passage and the second flow passage, under the disturbance of the ripple structure, the fluid continuously generates axial vortex and radial turbulence in the flow channel, the fluid can fully exchange heat in the flow channel, and the formation of scale layers in the flow channel is reduced, so that the heat exchange efficiency can be improved on one hand, and the service life of the heat exchanger can be prolonged on the other hand.

Description

Spiral plate heat exchanger and heat exchange device for large flow and high viscosity fluid

Technical Field

The invention relates to the technical field of heat exchangers, and in particular to a spiral plate heat exchanger and a heat exchange device for large-flow and high-viscosity fluids.

Background Art

At present, the heat exchange of large flow and high viscosity fluids is mostly done by shell-and-tube heat exchangers or spiral plate heat exchangers. The shell-and-tube heat exchanger is an inner and outer tube structure, and two fluids with different temperatures flow in the inner and outer tubes to achieve the effect of heat exchange; the spiral plate heat exchanger is made of two parallel metal plates rolled to form two independent channels, and two fluids with different temperatures flow in the two channels to achieve the effect of heat exchange.

However, the above-mentioned shell-and-tube heat exchanger occupies a large area and has low heat exchange efficiency. In order to increase efficiency, S-shaped tubes are often used instead of straight tubes. However, scale is easily accumulated at the elbows of the S-shaped tubes, which also affects the heat exchange efficiency.

The above-mentioned spiral plate heat exchanger also has the problems of small heat exchange area and low heat exchange efficiency.

Summary of the invention

Based on the above problems, the present invention provides a spiral plate heat exchanger and a heat exchange device for large flow and high viscosity fluids to solve the problem of low heat exchange efficiency of the current heat exchanger.

A first aspect of the present invention provides a spiral plate heat exchanger for high-flow and high-viscosity fluids, comprising a cylindrical shell, wherein a first flow channel and a second flow channel which are not connected to each other and are spirally arranged in the shell, wherein the first flow channel and the second flow channel are formed by two parallel heat exchange plates winding around each other from the center of the shell outward along the radial direction of the shell, wherein the inner spiral ends of the first flow channel and the second flow channel are separated by a partition, and the outer spiral ends of the first flow channel and the second flow channel are respectively sealed and connected to the arc-shaped side wall of the shell;

The first inlet of the first flow channel is arranged at the center of one end of the shell, the first outlet of the first flow channel is arranged on the arc-shaped side wall of the shell, the second inlet of the second flow channel is arranged on the arc-shaped side wall of the shell, and the second outlet of the second flow channel is arranged at the center of the other end of the shell;

Corrugations are provided on the first wall surface and/or the second wall surface of the first flow channel and the second flow channel, and the extension direction of the corrugations is parallel to the axis of the shell.

According to the spiral plate heat exchanger for high-flow and high-viscosity fluids provided by the present invention, a flow disturbance structure is provided on the wall surface of the first flow channel and the second flow channel, and the flow disturbance direction of the flow disturbance structure is perpendicular to the extension direction of the corrugation.

According to the spiral plate heat exchanger for high-flow and high-viscosity fluids provided by the present invention, the flow-disturbing structure includes a plurality of flow-disturbing protrusions arranged at equal intervals, and the flow-disturbing direction of each of the flow-disturbing protrusions is perpendicular to the extension direction of the corrugation.

According to the spiral plate heat exchanger for high-flow and high-viscosity fluids provided by the present invention, a chamfer is provided at the position where each of the flow-disturbing protrusions is connected to the wall surface.

According to the spiral plate heat exchanger for high-flow and high-viscosity fluids provided by the present invention, the first flow channel is a hot medium flow channel, the second flow channel is a cold medium flow channel, and the width of the first flow channel is greater than the width of the second flow channel.

According to the spiral plate heat exchanger for high-flow and high-viscosity fluids provided by the present invention, a plurality of distance columns are provided in the first flow channel and the second flow channel, and the axial direction of the distance columns is perpendicular to the axial direction of the shell.

According to the spiral plate heat exchanger for high-flow and high-viscosity fluids provided by the present invention, a plurality of the distance columns are evenly spaced apart in the axial direction and radial direction of the shell in the first flow channel and the second flow channel.

According to the spiral plate heat exchanger for high-flow and high-viscosity fluids provided by the present invention, in the axial cross-sectional direction of the shell, the angle between each of the distance columns is 60°.

According to the spiral plate heat exchanger for high-flow and high-viscosity fluids provided by the present invention, discharge ports are provided at the first outlet of the first flow channel and the second inlet of the second flow channel, and the discharge ports are used to clean blockages in the first flow channel and the second flow channel.

A second aspect of the present invention provides a heat exchange device, comprising the spiral plate heat exchanger for high-flow and high-viscosity fluids as described above.

Beneficial effects: The spiral plate heat exchanger for high-viscosity fluids with large flow rates provided by the present invention has a corrugated structure arranged on the wall surfaces of the first flow channel and the second flow channel. When the fluid flows on the corrugations, it is disturbed by the crests and troughs in the corrugations, which will generate axial vortices. Then, under the action of gravity and the axial vortices, the fluid will generate turbulence in the flow channel formed by radial spiral force, which increases the turbulence intensity near the flow channel wall and the heat supply capacity of the turbulence, so that the two fluids can fully exchange heat in the flow channel; under the action of continuous axial vortices and radial turbulence, the dirt deposited in the flow channel can be washed away, reducing the formation of scale layers in the flow channel, which can improve the heat exchange efficiency on the one hand and improve the service life of the heat exchanger on the other hand. Furthermore, since the corrugated structure is arranged on the flow channel wall, the heat exchange area in the flow channel can be effectively increased, further improving the heat exchange efficiency.

Furthermore, in the heat exchange device provided by the present invention, since it is provided with the spiral plate heat exchanger for high-flow and high-viscosity fluids as described above, it also has the various advantages as described above.

BRIEF DESCRIPTION OF THE DRAWINGS

In order to more clearly illustrate the technical solutions in the present invention or the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

FIG1 is a schematic diagram of the overall structure of a spiral plate heat exchanger for high-flow and high-viscosity fluids according to an embodiment of the present invention;

FIG2 is a schematic diagram of the overall structure of a spiral plate heat exchanger for high-flow and high-viscosity fluids according to an embodiment of the present invention;

3 is a radial cross-sectional view of a spiral plate heat exchanger for high-flow and high-viscosity fluids according to an embodiment of the present invention;

FIG4 is an overall structural diagram of the first flow channel and the second flow channel in an embodiment of the present invention;

FIG. 5 is an axial cross-sectional view of the first flow channel and the second flow channel in an embodiment of the present invention.

Reference numerals:

1. Shell; 2. First flow channel; 21. First inlet; 22. First outlet; 3. Second flow channel; 31. Second inlet; 32. Second outlet; 4. Heat exchange plate; 41. Flow spoiler; 5. Partition; 6. Spacer column; 7. Discharge port.

DETAILED DESCRIPTION

In order to make the purpose, technical solution and advantages of the present invention clearer, the technical solution of the present invention will be clearly and completely described below in conjunction with the drawings of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

In the description of the present invention, it is necessary to understand that the terms "upper", "lower", "horizontal", "inside", "outside", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, the meaning of "plurality" is two or more, unless otherwise clearly and specifically defined.

In order to make the purpose, technical solutions and advantages of the present invention more clearly understood, the present invention is further described in detail below in conjunction with the accompanying drawings and embodiments.

At present, the heat exchange of large flow and high viscosity fluids is mostly done by shell-and-tube heat exchangers or spiral plate heat exchangers. The shell-and-tube heat exchanger is an inner and outer tube structure, and two media with different temperatures flow in the inner and outer tubes to achieve the effect of heat exchange; the spiral plate heat exchanger is made of two parallel metal plates rolled to form two independent channels, and two media with different temperatures flow in the two channels to achieve the effect of heat exchange.

However, the above-mentioned shell-and-tube heat exchanger occupies a large area and has low heat exchange efficiency. In order to increase efficiency, S-shaped tubes are often used instead of straight tubes. However, scale is easily accumulated at the elbows of the S-shaped tubes, which also affects the heat exchange efficiency.

The above-mentioned spiral plate heat exchanger also has the problems of small heat exchange area and low heat exchange efficiency.

In the embodiment of the present invention, by providing a corrugated structure on the wall surface of the first flow channel and the second flow channel, when the fluid flows on the corrugations, it is disturbed by the crests and troughs in the corrugations, and an axial vortex will be generated. Then, under the action of gravity and the axial vortex, the fluid will generate turbulence in the flow channel formed by radial spiral force, which increases the turbulence intensity near the flow channel wall surface and the heat supply capacity of the turbulence, so that the two fluids can fully exchange heat in the flow channel. Under the action of continuous axial vortices and radial turbulence, the dirt deposited in the flow channel can be washed away, and the formation of scale layer in the flow channel can be reduced. On the one hand, the heat exchange efficiency can be improved, and on the other hand, the service life of the heat exchanger can be improved. Furthermore, since a corrugated structure is provided on the flow channel wall surface, the heat exchange area in the flow channel can be effectively increased, and the heat exchange efficiency can be further improved.

The spiral plate heat exchanger and heat exchange device for high-flow and high-viscosity fluids of the present invention will be described in detail below with reference to FIGS. 1 to 5 .

In a first aspect, an embodiment of the present invention provides a spiral plate heat exchanger for high-flow and high-viscosity fluids.

As shown in Fig. 1 and Fig. 4, a spiral plate heat exchanger for high-flow and high-viscosity fluids includes a shell 1, which is a cylindrical closed structure, that is, it includes an arc-shaped side wall and end walls arranged at both ends of the side wall in the axial direction, and there is a receiving cavity inside the shell 1. The spiral plate heat exchanger for high-flow and high-viscosity fluids is in a horizontal state when working, that is, the axis of the shell 1 is parallel to the ground.

The shell 1 is provided with a first flow channel 2 and a second flow channel 3 which are in a spiral shape and are not connected to each other. The first flow channel 2 and the second flow channel 3 are formed by two parallel heat exchange plates 4 which are wound around each other from the center of the shell 1 to the outside along the radial direction of the shell 1. The winding can be performed clockwise or counterclockwise, which is not limited in this embodiment. The inner spiral ends of the first flow channel 2 and the second flow channel 3 are separated by a partition 5 so that the first flow channel 2 and the second flow channel 3 are not connected to each other. The outer spiral ends of the first flow channel 2 and the second flow channel 3 are respectively sealed and connected to the arc-shaped side wall of the shell 1. The axial ends of the first flow channel 2 and the second flow channel 3 are respectively sealed and connected to the end walls of the axial ends of the shell 1 so that the first flow channel 2 and the second flow channel 3 are not connected to each other.

The first inlet 21 of the first flow channel 2 is arranged at the center of one end of the shell 1, that is, the center of one of the end walls of the shell 1, the first outlet 22 of the first flow channel 2 is arranged on the arc-shaped side wall of the shell 1, the second inlet 31 of the second flow channel 3 is arranged on the arc-shaped side wall of the shell 1, and the second outlet 32 of the second flow channel 3 is arranged at the center of the other end of the shell 1, that is, the center of the other end wall of the shell 1.

In one of the embodiments, corrugations are provided on the first wall surface or the second wall surface of the first flow channel 2 and the second flow channel 3. It can be understood that corrugations are provided on one of the wall surfaces of the two heat exchange plates 4 used to form the first flow channel 2 and the second flow channel 3. Specifically, the corrugations can be formed by pressing on the heat exchange plate 4 using a pressing roller.

In another embodiment, corrugations are provided on the first wall surface and the second wall surface of the first flow channel 2 and the second flow channel 3. It can be understood that corrugations are provided on the two wall surfaces of the flow channels formed by the two heat exchange plates 4. Specifically, a pressure roller can be used to directly press the heat exchange plate 4 into a corrugated plate for winding to form the first flow channel 2 and the second flow channel 3.

Whether corrugations are provided on one or both walls of the first flow channel 2 and the second flow channel 3 , the extension direction of the corrugations is parallel to the axis of the shell 1 . It can be understood that the superimposed arrangement direction of the crests and troughs in the corrugations is along the extension direction of the axis of the shell 1 .

The specific working process is: the first flow channel 2 is set as a hot flow channel, the second flow channel 3 is set as a cold flow channel, and a large flow of high-viscosity fluid enters the second flow channel 3 to fully exchange heat with the hot fluid in the first flow channel 2. The hot fluid first enters the first flow channel 2 to preheat the flow channel, and after the preheating is completed, the high-viscosity fluid enters the second flow channel 3 for heat exchange.

When the hot fluid and the high-viscosity fluid enter the first flow channel 2 and the second flow channel 3 respectively, the spiral plate heat exchanger works in a horizontal state, and the fluid will first flow along the axial direction of the shell 1. Since the walls of the first flow channel 2 and the second flow channel 3 are provided with corrugations, and the extension direction of the corrugations is parallel to the axis of the shell 1, when the fluid flows on the corrugations, it is disturbed by the crests and troughs in the corrugations, and axial vortices will be generated. Then, under the action of gravity and axial vortices, the fluid will generate turbulence formed by radial spiral force in the flow channel, which increases the turbulence intensity and heat supply capacity of the turbulence near the flow channel wall, so that the two fluids can fully exchange heat in the flow channel. Under the action of continuous axial vortices and radial turbulence, the dirt deposited in the flow channel can be washed away, reducing the formation of scale layers in the flow channel. On the one hand, the heat exchange efficiency can be improved, and on the other hand, the service life of the heat exchanger can be improved. Furthermore, since a corrugated structure is provided on the flow channel wall, the heat exchange area in the flow channel can be effectively increased, further improving the heat exchange efficiency.

In this embodiment, by providing a corrugated structure on the wall surface of the first flow channel 2 and the second flow channel 3, when the fluid flows on the corrugations, it is disturbed by the crests and troughs in the corrugations, and an axial vortex will be generated. Then, under the action of gravity and the axial vortex, the fluid will generate turbulence in the flow channel formed by radial spiral force, which increases the turbulence intensity near the flow channel wall surface and the heat supply capacity of the turbulence, so that the two fluids can fully exchange heat in the flow channel. Under the action of continuous axial vortices and radial turbulence, the dirt deposited in the flow channel can be washed away, reducing the formation of scale layer in the flow channel. On the one hand, the heat exchange efficiency can be improved, and on the other hand, the service life of the heat exchanger can be improved. Furthermore, since a corrugated structure is provided on the flow channel wall surface, the heat exchange area in the flow channel can be effectively increased, further improving the heat exchange efficiency.

In another embodiment, a corrugated structure is provided on both wall surfaces of the first flow channel 2 and the second flow channel 3. The double-sided corrugated structure can effectively improve the stress distribution at the inner wall surface of the tube, further improve the disturbance effect of the axial vortex and radial turbulence, improve the heat exchange efficiency, and also reduce the formation of wall scale, thereby effectively improving the service life of the heat exchanger.

As shown in Fig. 5, in some embodiments of the present invention, a flow-disturbing structure is further provided on the wall surface of the first flow channel 2 and the second flow channel 3, and the flow-disturbing direction of the flow-disturbing structure is perpendicular to the extension direction of the corrugation. Specifically, the flow-disturbing structure can be set as a flow-disturbing corrugation, and the flow-disturbing direction of the flow-disturbing corrugation is perpendicular to the extension direction of the corrugation in the previous embodiment, that is, in the previous embodiment, the superimposed arrangement direction of the crests and troughs in the corrugation is along the axial extension direction of the shell 1, and the superimposed arrangement direction of the crests and troughs in the flow-disturbing corrugation is along the radial direction of the shell 1, so that the flow-disturbing direction of the flow-disturbing corrugation is perpendicular to the extension direction of the corrugation.

In some other embodiments, the spoiler structure may also be provided as a spoiler rib, and the spoiler direction of the spoiler rib is perpendicular to the extension direction of the corrugation.

In this embodiment, a spoiler structure is arranged on the wall surface of the first flow channel 2 and the second flow channel 3, and the spoiler direction of the spoiler structure is perpendicular to the extension direction of the corrugation, that is, the spoiler direction of the spoiler structure is perpendicular to the spoiler direction of the corrugated structure, thereby further improving the spoiler effect in the first flow channel 2 and the second flow channel 3 to improve the heat exchange efficiency.

As shown in Figure 5, the spoiler structure specifically includes a plurality of spoiler protrusions 41 arranged at equal intervals, and the spoiler direction of each spoiler protrusion 41 is perpendicular to the extension direction of the corrugation. Relative to the axial direction of the shell 1, each spoiler protrusion 41 extends to the two end walls of the shell 1, and relative to the first flow channel 2 and the second flow channel 3, a plurality of spoiler protrusions 41 are arranged on the wall surface at equal intervals along the spiral shape of the first flow channel 2 and the second flow channel 3. The spoiler direction of the spoiler protrusion 41 is perpendicular to the extension direction of the corrugation, that is, the spoiler direction of the spoiler structure is perpendicular to the spoiler direction of the corrugated structure. By arranging the spoiler protrusion 41 and the corrugated structure double spoiler structure in the first flow channel 2 and the second flow channel 3, the spoiler protrusion 41 and the corrugated structure form a mutually perpendicular double spoiler effect, further improving the spoiler effect in the first flow channel 2 and the second flow channel 3, so as to improve the heat exchange efficiency.

Furthermore, in order to reduce the formation of a recirculation zone at the connection between the spoiler protrusion 41 and the wall of the flow channel, thereby affecting its heat exchange effect, and in order to effectively reduce the stress generated by the fluid on the wall, in an embodiment of the present invention, a chamfer is set at the position where each spoiler protrusion 41 is connected to the wall of the first flow channel 2 and the second flow channel 3.

In some other embodiments of the present invention, the first flow channel 2 is a hot fluid flow channel, and the second flow channel 3 is a cold fluid flow channel. The hot fluid enters the flow channel through the first inlet 21 of the first flow channel 2 to preheat the flow channel, and the hot fluid flows out through the first outlet 22 on the side wall of the shell 1. The hot fluid enters from the center of the shell 1 and is gradually preheated from the center to the outer edge. The flow direction of the hot fluid is also from the center to the outer edge. The high-viscosity fluid with a large flow rate is a cold fluid, which enters from the second inlet 31 of the second flow channel 3 on the side wall of the shell 1 and flows out from the second outlet 32 in the center of the shell 1. The first outlet 22 and the second outlet 32 are arranged opposite to each other, and the flow direction of the cold fluid is from the outer edge to the center, which is opposite to the flow direction of the hot fluid, thereby realizing the reverse flow of the two fluids, which can further improve the heat exchange efficiency.

Moreover, the width of the first flow channel 2 is greater than that of the second flow channel 3. Specifically, the width of the first flow channel 2 can be set to 1.5 to 2 times the width of the second flow channel 3, so that the unit flow volume of the hot fluid is greater than the unit flow volume of the cold fluid, which is more conducive to sufficient heat exchange between the hot and cold fluids and improves the heat exchange efficiency.

As shown in Figures 4 and 5, in order to ensure the stability of the flow channel width of the first flow channel 2 and the second flow channel 3, in some embodiments of the present invention, a plurality of distance columns 6 are provided in the first flow channel 2 and the second flow channel 3, and the plurality of distance columns 6 are evenly spaced in the first flow channel 2 and the second flow channel 3 along the axial and radial directions of the shell 1. The axial direction of the distance columns 6 is perpendicular to the axial direction of the shell 1, and the two ends of the distance columns 6 are respectively connected to the two wall surfaces of the two flow channels. On the one hand, the distance columns 6 are used to distance and support the flow channel width of the first flow channel 2 and the second flow channel 3 to ensure the stability of the flow channel width of the first flow channel 2 and the second flow channel 3; on the other hand, the distance columns 6 also have a disturbing effect on the flow channel in the flow channel, forming a "triple disturbing effect" together with the corrugated structure and the spoiler protrusion 41 in the aforementioned embodiment, so that the fluid forms a mixed flow in the flow channel, thereby enhancing the heat exchange effect.

Furthermore, as shown in FIG. 5 , in the axial cross-sectional direction of the shell 1 , the angle between each distance column 6 is 60°, which can form a mixed flow in the flow channel to form a regular turbulence, thereby ensuring the stability of the heat exchange effect.

As shown in Figures 1 and 2, a discharge port 7 is provided at the first outlet 22 of the first flow channel 2 and the second inlet 31 of the second flow channel 3. The discharge port 7 is used to clear blockages in the first flow channel 2 and the second flow channel 3. When the first flow channel 2 or the second flow channel 3 is blocked, the discharge port 7 can be opened to clear the blockage.

In a second aspect, an embodiment of the present invention further provides a heat exchange device, including a spiral plate heat exchanger for high-flow and high-viscosity fluids provided in any of the above embodiments. The derivation process of the beneficial effects of the heat exchange device in the embodiment of the present invention is generally similar to the derivation process of the beneficial effects of the spiral plate heat exchanger for high-flow and high-viscosity fluids described above, so it will not be repeated here.

Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims (10)

1. A spiral plate heat exchanger for high-flow and high-viscosity fluids, characterized in that it comprises a cylindrical shell (1), wherein a first flow channel (2) and a second flow channel (3) which are not connected to each other and are in a spiral shape are provided in the shell (1), wherein the first flow channel (2) and the second flow channel (3) are formed by two parallel heat exchange plates (4) which are wound around each other from the center of the shell (1) to the outside along the radial direction of the shell (1), wherein the inner spiral ends of the first flow channel (2) and the second flow channel (3) are separated by a partition (5), and the outer spiral ends of the first flow channel (2) and the second flow channel (3) are respectively sealed and connected to the arc-shaped side wall of the shell (1); The first inlet (21) of the first flow channel (2) is arranged at the center of one end of the shell (1), the first outlet (22) of the first flow channel (2) is arranged on the arc-shaped side wall of the shell (1), the second inlet (31) of the second flow channel (3) is arranged on the arc-shaped side wall of the shell (1), and the second outlet (32) of the second flow channel (3) is arranged at the center of the other end of the shell (1); Corrugations are provided on the first wall surface and/or the second wall surface of the first flow channel (2) and the second flow channel (3), and the extension direction of the corrugations is parallel to the axis of the shell (1). 2. The spiral plate heat exchanger for high-flow and high-viscosity fluids according to claim 1 is characterized in that a spoiler structure is provided on the wall surface of the first flow channel (2) and the second flow channel (3), and the spoiler direction of the spoiler structure is perpendicular to the extension direction of the corrugation. 3. The spiral plate heat exchanger for high-flow and high-viscosity fluids according to claim 2 is characterized in that the spoiler structure includes a plurality of spoiler protrusions (41) arranged at equal intervals, and the spoiler direction of each spoiler protrusion (41) is perpendicular to the extension direction of the corrugation. 4. The spiral plate heat exchanger for high-flow and high-viscosity fluids according to claim 3 is characterized in that a chamfer is provided at the position where each of the flow-disturbing protrusions (41) is connected to the wall surface. 5. A spiral plate heat exchanger for high-flow and high-viscosity fluids according to any one of claims 1 to 4, characterized in that the first flow channel (2) is a hot fluid flow channel, the second flow channel (3) is a cold fluid flow channel, and the width of the first flow channel (2) is greater than the width of the second flow channel (3). 6. The spiral plate heat exchanger for high-flow and high-viscosity fluids according to claim 5 is characterized in that a plurality of distance columns (6) are provided in the first flow channel (2) and the second flow channel (3), and the axial direction of the distance columns (6) is perpendicular to the axial direction of the shell (1). 7. The spiral plate heat exchanger for high-flow and high-viscosity fluids according to claim 6 is characterized in that a plurality of the distance columns (6) are evenly spaced in the first flow channel (2) and the second flow channel (3) along the axial and radial directions of the shell (1). 8. The spiral plate heat exchanger for high-flow and high-viscosity fluids according to claim 6 or 7, characterized in that, in the axial cross-sectional direction of the shell (1), the angle between each of the distance columns (6) is 60°. 9. A spiral plate heat exchanger for high-flow and high-viscosity fluids according to any one of claims 1 to 4, characterized in that a discharge port (7) is provided at the first outlet (22) of the first flow channel (2) and the second inlet (31) of the second flow channel (3), and the discharge port (7) is used to clean blockages in the first flow channel (2) and the second flow channel (3). 10. A heat exchange device, characterized in that it comprises the spiral plate heat exchanger for high-flow and high-viscosity fluids according to any one of claims 1 to 9.