Heating device

Abstract

The present disclosure relates to a heating device. The heating device comprises a heating plate and a housing having an inlet and an outlet, wherein the heating plate is arranged on one side of the housing to close the housing; and at least one first flow channel is formed in the housing, and a fluid to be heated flows from the inlet to the outlet via the first flow channel. A turbulent structure is provided in the first flow channel, the turbulent structure is constructed as a protruding rib plate formed on an inner wall of the first flow channel, and the protruding rib plate spirally extends in an extension direction of the first flow channel, so as to disturb the flowing of fluid in the first flow channel. The heating device provided in the present disclosure enables the fluid to maintain uniform heat exchange between each portion thereof and the heating plate, thereby reducing the production cost of the heating device, and enhancing the heating performance of the heating device.

Description

Heating device Technical Field

[0001] The present disclosure relates to the field of vehicles, and in particular, to a heating device. Background Art

[0002] In traditional transportation, a car's thermal circulation system typically heats a target area by transferring heat energy from a high-temperature fluid through heat exchange. Compared to direct electrical heating, this method is more efficient, environmentally friendly, and safer.

[0003] However, during the process of fluid temperature exchange, the efficiency of temperature replacement is often reduced due to incomplete and unbalanced heat exchange, resulting in poor final heat exchange effect. Technical personnel in this field have tried to adopt various methods to improve the efficiency of temperature replacement, but as the efficiency of temperature replacement increases, the production cost also increases, and the reduction in fluid flow rate caused by the improvement of temperature replacement efficiency also leads to a decrease in the heating performance of the heating device. Utility Model Content

[0004] The present disclosure aims to improve the heating performance of a heating device while ensuring uniform heat exchange of a fluid.

[0005] In a first aspect, the present disclosure provides a heating device, comprising a heating plate and a shell having an inlet and an outlet, the heating plate being arranged on one side of the shell to close the shell; at least one first flow channel is formed in the shell, and the fluid to be heated flows from the inlet to the outlet through the first flow channel, wherein a disruptive flow structure is arranged in the first flow channel, and the disruptive flow structure is constructed as a raised rib formed on the inner wall of the first flow channel, and the raised rib extends spirally along the extension direction of the first flow channel to disrupt the flow of the fluid in the first flow channel.

[0006] When the fluid flows smoothly along the flow channel, it is easy to enter a laminar state, and at this time, it is not easy for the fluid to mix between the layers. Specifically, the fluid layer close to the heating plate is easier to heat, and the fluid layer far away from the heating plate is more difficult to heat. Ultimately, the fluid between the layers is difficult to achieve the desired heat exchange effect due to uneven heating. In order to prevent the fluid from entering a laminar state, a heating device provided in this example includes a disturbing structure in the first flow channel, so that when the fluid flows in the first flow channel, the fluid contacts the disturbing structure in a laminar state, and is disturbed by the disturbing structure, so that the fluid enters a turbulent state from a laminar state. The fluid in the first flow channel can also contact the heating plate alternately and repeatedly in a turbulent state, thereby achieving uniform heating of the fluid by the heating plate, improving the heat exchange speed of the fluid, and thereby improving the heat exchange efficiency of the fluid.

[0007] The flow-disturbing structure is constructed as a raised rib formed on the inner wall of the first flow channel, which can be understood as the flow-disturbing structure being formed integrally with the first flow channel, thereby reducing the production cost of the heating device.

[0008] The helically extending flow-turbulating structure reduces the contact area between the flow-turbulating structure and the fluid on a plane perpendicular to the flow direction of the fluid at the same time, thereby reducing the flow resistance of the fluid flowing through the flow-turbulating structure.

[0009] The flow-disturbing structure, which spirally extends along the direction of the first flow channel, allows the fluid flowing through it to simultaneously generate a spiraling effect while flowing along the direction of the first flow channel. This rotation removes any bubbles that may be present within the first flow channel, thereby increasing the lifespan of the heating device. This also eliminates the need for additional venting holes within the heating device, simplifies the heating device's structure, and further reduces production costs.

[0010] In the spiral forward state, the fluid can not only maintain uniform heat exchange between each part of the fluid and the heating plate, but also ensure that it flows through the first flow channel at a relatively fast speed, thereby improving the heating level of the heating device as a whole and enhancing the heating performance of the heating device.

[0011] In an exemplary embodiment, a flow guiding space is provided in the shell, and the at least one first flow channel is provided as a plurality of first flow channels separated from each other in the flow guiding space, and a flow disturbing structure is provided in each first flow channel.

[0012] Within the same flow range, the greater the number of first flow channels, the better the disturbing effect of the flow-disturbing structure on the fluid.

[0013] In an exemplary embodiment, the housing defines an inlet and an outlet, wherein a cross-sectional area of ​​the inlet and / or the outlet perpendicular to a flow direction of the fluid is smaller than a cross-sectional area / a sum of cross-sectional areas of the at least one first flow channel.

[0014] To further increase the fluid's residence time within the first flow channel and thereby enhance the heat exchange effect, the sum of the cross-sectional areas of the multiple first flow channels is set to be larger than the cross-sectional area of ​​the inlet / outlet. This slows the flow rate of the fluid within the multiple first flow channels compared to the flow rate of the fluid flowing through the inlet / outlet, further increasing the contact time between the fluid and the first flow channels. At the same time, the larger sum of the total cross-sectional areas results in a larger fluid flow area. In other words, the first flow channels occupy a larger space within the flow guide space, which also results in a larger contact area between the fluid and the shell. These features further enhance the heat exchange effect of the fluid.

[0015] In an exemplary embodiment, the shell has multiple bars formed in the guide space to form multiple first flow channels, each bar separates two adjacent first flow channels, wherein the heating plate abuts the multiple bars, or a flow gap is set between the heating plate and the multiple bars.

[0016] When the heating plate abuts against the multiple bars, that is, when the heating plate abuts against the top of the multiple bars, there is no gap between the heating plate and the first flow channel. When the space occupied by the first flow channel is large enough, the desired fluid heat exchange efficiency is met. At this time, in order to ensure that the heating device maintains a high heating level, the fluid in the first flow channel needs to have a faster flow rate. By setting the heating plate to abut against the bars (that is, the flow of fluids between the multiple first flow channels does not interfere with each other), the flow rate of the fluid in the first flow channel is faster, while ensuring the heat exchange efficiency of the fluid, the heating level of the air in the heating device is further improved. When a flow gap is set between the heating plate and the first flow channel, that is, the heating plate does not abut against the bars. When the space occupied by the first flow channel is small due to design factors, in order to ensure that the fluid can reach a good heat exchange level before flowing out of the guide space, it is necessary to increase the disturbance level of the fluid in the multiple first flow channels to achieve a higher fluid heat exchange level. By arranging the heating plate so that there is a flow gap between the heating plate and the grid bars (ie, the flow of the fluids between the multiple first flow channels can affect each other), the fluids in the multiple first flow channels can be further disturbed, thereby improving the heat exchange level of the fluids.

[0017] In an exemplary embodiment, each of the plurality of first flow channels is constructed to be symmetrical about a first direction or to be centrally symmetrical about itself. The housing further includes a plurality of guide plates within the flow guide space to form a plurality of second flow channels. An inlet is formed on an inner wall of the housing, the inlet being oriented substantially perpendicular to the first direction. The plurality of guide plates include a first guide plate extending between the inlet and the plurality of bars. An end of the first guide plate, distal from the plurality of bars, is arranged to gradually rise in the first direction, or to gradually and evenly rise, along the direction of the inlet.

[0018] When a fluid with a certain impact force flows into the guide space from the inlet, due to its certain initial velocity, the fluid will tend to flow toward the first flow channel away from the inlet, causing the fluid in the first flow channel away from the inlet to accelerate its outflow speed from the liquid outlet of the first flow channel due to excessive fluid flow when the expected heat exchange effect is not achieved; on the contrary, the first flow channel close to the inlet receives less fluid, so the fluid therein slows down its outflow speed from the liquid outlet of the first flow channel due to less flow when the expected heat exchange effect has been achieved. Therefore, the present disclosure sets a first guide plate between the inlet and the multiple bars, and the direction of the inlet is basically perpendicular to the first direction, which can block the fluid from impacting the guide plate. The first guide plate that gradually rises in the first direction along the direction of the inlet allows the fluid to impact each guide plate without being blocked, and then enters each second flow channel, so that the fluid can flow into the corresponding first flow channel along the second flow channel formed by the first guide plate. The outflow speed from the liquid outlet of the multiple first flow channels can be adjusted. The first guide plates that rise at equal intervals in the first direction toward the inlet ensure that each guide surface receives a relatively uniform amount of fluid from the inlet, ie, the amount of fluid introduced into the first flow channel via the second flow channel is also relatively uniform.

[0019] The outlet is formed on the inner wall of the shell, and the direction of the outlet is basically perpendicular to the first direction. The multiple guide plates include a second guide plate extending between the outlet and the multiple bars, and the end of the second guide plate away from the multiple bars is arranged to gradually and evenly rise in the first direction along the direction of the outlet. When the fluid flows from the first flow channel to the outlet through the second flow channel formed by the second guide plate, the second guide plate gradually rising in the first direction along the direction of the outlet prevents the fluid from being blocked when flowing out of the second flow channel and heading towards the outlet and flowing back into the first flow channel. The second guide plates rising at equal intervals in the first direction along the direction of the outlet can also play the same role as the first guide plate when the positions of the inlet and outlet need to be swapped due to actual installation reasons.

[0020] The first flow channel that is symmetrical about the first direction or symmetrical about its own center can have the inlet and the outlet used interchangeably.

[0021] In an exemplary embodiment, the shell has a plurality of bars formed in the guide space to form a plurality of first flow channels, each of the first flow channels is constructed to be symmetrical about the first direction or to be centrally symmetrical about itself, and the shell also has a plurality of guide plates formed in the guide space to form a plurality of second flow channels. An inlet is formed on the inner wall of the shell, the direction of the inlet is substantially perpendicular to the first direction, the plurality of guide plates include a first guide plate extending between the inlet and the plurality of bars, the end of the first guide plate away from the plurality of bars is arranged to gradually rise in the first direction along the direction of the inlet, or gradually and evenly spaced, and each of the first guide plates includes a first portion and a second portion away from the plurality of first flow channels in sequence, the first portion of the first guide plate extending along the first direction, and the second portion of the first guide plate being constructed to be in the shape of an arc bent toward the inlet. When a fluid with a certain impact force flows into the guide space from the inlet, due to its certain initial velocity, the fluid will tend to flow toward the first flow channel away from the inlet, causing the fluid in the first flow channel away from the inlet to accelerate its outflow speed from the liquid outlet of the first flow channel due to excessive fluid flow when the expected heat exchange effect is not achieved; on the contrary, the first flow channel close to the inlet receives less fluid, so the fluid therein slows down its outflow speed from the liquid outlet of the first flow channel due to less flow when the expected heat exchange effect has been achieved. Therefore, the present invention sets a first guide plate between the inlet and the multiple bars, and the direction of the inlet is basically perpendicular to the first direction, which can block the fluid that impacts the guide plate. The first guide plate that gradually rises in the first direction along the direction of the inlet can allow the fluid to impact each guide plate without being blocked, and then enter each second flow channel, so that the fluid can flow into the corresponding first flow channel along the second flow channel formed by the first guide plate. The outflow speed from the liquid outlet of the multiple first flow channels can be adjusted. When fluid enters the guide plate from the inlet, a guide plate that is substantially perpendicular to the inlet can easily cause fluid splashing, affecting uniform distribution across the multiple first flow channels. In the present disclosure, the second portion of the guide plate, which is configured as an arc curved toward the inlet, effectively prevents splashing when impacted by fluid, ensuring uniform distribution across the multiple first flow channels.

[0022] The outlet is formed on the inner wall of the shell, and the direction of the outlet is basically perpendicular to the first direction. The multiple guide plates include a second guide plate extending between the outlet and the multiple bars. The end of the second guide plate away from the multiple bars is arranged to gradually rise in the first direction along the direction of the outlet, or gradually and evenly spaced. Each guide plate in the second guide plate includes a first part and a second part away from the multiple first flow channels. The first part of the second guide plate extends along the first direction, and the second part of the second guide plate is constructed to be curved toward the outlet. When the fluid flows from the first flow channel to the outlet through the second flow channel formed by the second guide plate, the second guide plate that gradually rises in the first direction along the direction of the outlet prevents the fluid from being blocked and flowing back into the first flow channel when it flows out of the second flow channel and toward the outlet. The guide plate with an arc structure facing the outlet can also guide the fluid to flow out toward the outlet, reducing the time that the fluid that has achieved the expected heat exchange effect stays in the guide space.

[0023] The first flow channel that is symmetrical about the first direction or symmetrical about its own center can have the inlet and the outlet used interchangeably.

[0024] In an exemplary embodiment, the ends of the multiple guide plates near the multiple bars are aligned with the ends of the multiple bars near the multiple guide plates. Given a large flow-guiding space, rapid fluid exit from the flow-guiding space while achieving the desired heat exchange effect can provide a higher level of heating for subsequent devices. This arrangement allows for rapid fluid transfer from the second flow channel to the first flow channel, and vice versa.

[0025] In an exemplary embodiment, the ends of the plurality of guide plates near the plurality of bars are arranged in a staggered manner with the ends of the plurality of bars near the plurality of guide plates. When the guide space is small, increasing the retention time of the fluid in the guide space can enable the fluid to more effectively achieve the desired heat exchange effect. This arrangement can mix the fluids in the plurality of first flow channels, thereby increasing the heat exchange efficiency of the fluids between the plurality of first flow channels.

[0026] In an exemplary embodiment, a transverse channel is provided between the plurality of second flow channels and the plurality of first flow channels, and the transverse channel is configured to mix fluids flowing between the plurality of second flow channels and the plurality of first flow channels.

[0027] The fluid in the second flow channel is still in a laminar flow state before entering the first flow channel and contacting the flow-disturbing structure. The present disclosure provides a transverse channel between the second flow channel and the first flow channel, so that after passing through the transverse channel, the fluid is mixed as a whole and flows into the first flow channel in a turbulent state; and before flowing from the first flow channel into the second flow channel, the fluid is mixed again and finally mixed to maintain a turbulent state before flowing from the first flow channel into the second flow channel.

[0028] In an exemplary embodiment, the first flow channel extends in a circuitous manner. To avoid a short heat exchange time of the fluid resulting in low heat exchange efficiency, the circuitous extension of the first flow channel increases the contact time between the fluid and the first flow channel, further improving the heat exchange effect of the fluid. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] In order to more clearly illustrate the technical solutions of the embodiments of the present disclosure, the following briefly introduces the drawings required for use in the embodiments.

[0030] It should be understood that the following drawings only illustrate certain embodiments of the present disclosure and therefore should not be regarded as limiting the scope. A person of ordinary skill in the art can derive other relevant drawings based on these drawings without inventive effort.

[0031] It should be understood that the same or similar reference numerals are used in the drawings to represent the same or similar elements (components or components).

[0032] It should be understood that the drawings are merely schematic and that the sizes and proportions of elements (components or components) in the drawings are not necessarily accurate.

[0033] FIG1 is a schematic structural diagram of a heating device according to an embodiment of the present disclosure.

[0034] FIG2 is a schematic structural diagram of the heating device according to the embodiment of FIG1 , wherein the heating plate is not shown.

[0035] FIG. 2A is a schematic cross-sectional view of a first flow channel of the heating device of the embodiment of FIG. 1 .

[0036] FIG. 2B is a partially enlarged schematic diagram of the heating device of the embodiment of FIG. 1 .

[0037] FIG3 is an enlarged schematic diagram of the turbulence structure of the heating device of the embodiment of FIG1 .

[0038] FIG. 3A is a reference diagram of the spoiler structure of FIG. 3 .

[0039] FIG4 is a front view of the heating device of the embodiment of FIG1 .

[0040] FIG. 4A is a cross-sectional view taken along line AA in FIG. 4 .

[0041] FIG. 4B is a cross-sectional view taken along line AA in FIG. 4 .

[0042] FIG5 is a schematic structural diagram of the heating device of the embodiment of FIG1 .

[0043] FIG. 5A is a schematic diagram of a first guide plate among the guide plates shown in FIG. 5 in an embodiment.

[0044] FIG5B is a schematic diagram of a second guide plate among the guide plates shown in FIG5 under an embodiment.

[0045] FIG5C is a schematic diagram of the first guide plate in the guide plates shown in FIG5 under another embodiment.

[0046] FIG5D is a schematic diagram of the first guide plate in the guide plates shown in FIG5 under another embodiment.

[0047] FIG. 6 is a schematic diagram of the guide plate shown in FIG. 5 guiding the flow of fluid.

[0048] FIG7 is a diagram showing the layout relationship between the first flow channel and the second flow channel.

[0049] FIG8 is another layout relationship diagram of the first flow channel and the second flow channel. DETAILED DESCRIPTION

[0050] The following will be combined with the accompanying drawings in the embodiments of the present disclosure to clearly and completely describe the technical solutions in the embodiments of the present disclosure. Obviously, the embodiments described are only part of the embodiments of the present disclosure, not all of the embodiments.

[0051] As shown in Figures 1 to 3A, the heating device 10 of this embodiment includes a heating plate 200 and a shell 100 having an inlet 130 and an outlet 150. The heating plate 200 is arranged on one side of the shell 100 to close the shell; a first flow channel 120 is formed in the shell 100, and the fluid to be heated flows from the inlet 130 to the outlet 150 through the first flow channel 120, wherein a spoiler structure 140 is provided in the first flow channel 120, and the spoiler structure 140 is constructed as a raised rib formed on the inner wall of the first flow channel 120, and the raised rib extends spirally along the extension direction of the first flow channel 120 to disturb the flow of the fluid in the first flow channel 120.

[0052] Exemplarily, the inlet 130 and the outlet 150 are fluidically connected via the first flow channel 120, i.e., the first flow channel 120 extends from near the inlet 130 to near the outlet 150. The first flow channel 120 has a liquid inlet end 125 and a liquid outlet end 127, wherein the liquid inlet end 125 corresponds to the inlet 130, and the liquid outlet end 127 corresponds to the outlet 150. The fluid flows from the inlet 130 through the liquid inlet end 125, the first flow channel 120, the liquid outlet end 127, and finally out of the outlet 150. The first flow channel 120 is formed in the housing 100, wherein the distance from the heating plate 200 to the bottom of the housing 100 defines the maximum height of the first flow channel 120.

[0053] For example, FIG2A shows a schematic cross-sectional view of the first flow channel 120 along a first direction. The spoiler structure 140 covers the width of the first flow channel 120. In other examples, the spoiler structure may partially cover the width of the first flow channel. The height of the spoiler structure 140 does not exceed the height of the first flow channel 120. For example, the height of the spoiler structure 140 does not exceed 1 / 2, 1 / 3, or 1 / 4 of the height of the first flow channel 120.

[0054] The flow-disrupting structure 140 can be, for example, a segmented flow-disrupting structure (independently distributed at multiple locations within the first flow channel 120) (as shown in FIG1-2) or an integral flow-disrupting structure (one flow-disrupting structure 140 extends throughout the entire extension of the first flow channel 120). In the case of a segmented flow-disrupting structure, when the fluid flows in from the liquid inlet end 125, it is in a laminar flow state, and there is a temperature difference between the fluid layer near the housing 100 and the heating plate 200 and the fluid layer away from the housing 100 and the heating plate 200, and the heat exchange effect is poor. Continuing to flow along the first flow channel 120, the fluid first contacts the first spoiler structure 140. Under the disturbing action of the spoiler structure 140, the fluid in the laminar state enters the turbulent state. After passing the spoiler structure 140, the fluid tends to return from the turbulent state to the laminar state. Before returning to the laminar state, the fluid contacts the second spoiler structure 140, so that the turbulent state is maintained. At this rhythm, the fluid successively contacts the third, fourth, and Nth spoiler structures 140 until it flows out from the liquid outlet 127, and the fluid always remains in a turbulent state. In other embodiments, for example, when the spoiler structure 140 is an integral spoiler structure, when the fluid flows in from the liquid inlet end 125, the fluid that contacts the spoiler structure 140 enters a turbulent state. Because it always contacts the spoiler structure 140 during the flow in the first flow channel 120, its turbulent state is always maintained.

[0055] The heating device 10 provided in this embodiment enables the fluid to contact the disrupting structure 140 in a laminar state when flowing in the first flow channel 120. Under the disturbance effect of the disrupting structure 140, the fluid enters a turbulent state from a laminar state. The fluid in the first flow channel 120 can also contact the heating plate 200 alternately and repeatedly in the turbulent state, thereby achieving uniform heating of the fluid by the heating plate 200, improving the heat exchange speed of the fluid, and thereby improving the heat exchange efficiency of the fluid.

[0056] As shown in FIG2B , the spoiler structure 200 is constructed as a raised rib formed on the inner wall of the first flow channel 120. It can be understood that the spoiler structure 200 is formed integrally with the first flow channel 120. In this example, the spoiler structure 140 is formed on the bottom surface of the first flow channel 120. In other examples, the spoiler structure can also be formed on the inner surface of the first flow channel. The integral formation of the spoiler structure 200 and the first flow channel 120 can reduce the manufacturing cost of the heating device 10. At the same time, the integral formation can also increase the stability of the spoiler structure 200 and ensure stable spoiler efficiency.

[0057] In addition, since the heating plate 200 is in contact with the housing 100, while the heating plate 200 heats the fluid, it also heats the housing 100 to a certain extent. In the case where the flow-disrupting structure 200 is integrally formed with the first flow channel 120, the flow-disrupting structure 200 is also indirectly in contact with the housing 100, which means that the contact area between the fluid and the housing 100 is increased, further improving the heat exchange efficiency of the fluid, so that the heating device 10 can maintain a high heating level.

[0058] As shown in FIG. 3 and FIG. 3A , the spirally extending flow-disturbing structure 140 reduces the contact area between the flow-disturbing structure 140 and the fluid on a plane perpendicular to the fluid flow direction at the same time, thereby reducing the flow resistance of the fluid flowing through the flow-disturbing structure 140 .

[0059] Exemplarily, for example, starting and ending at both ends of the spoiler structure 140, the spoiler structure 140 has two or more liquid-guiding surfaces 142, and from one end to the other end of the liquid-guiding surface 142, the liquid-guiding surface 142 is a spiral curved surface. For example, the spiral curved surface can be a twisted curved surface, and along the direction perpendicular to the twisting direction, the normal angle of any part of each liquid-guiding surface 142 is different from the normal angle of other parts of the liquid-guiding surface 142. The spoiler structure 140 that extends spirally along the extension direction of the first flow channel 120 can make the fluid flowing through it produce a spiral forward effect while flowing along the extension direction of the first flow channel 120, and can take away any bubbles that may exist in the first flow channel 120 during the rotation process, thereby increasing the service life of the heating device 10. At the same time, it eliminates the need to add an exhaust hole structure inside the heating device 10, simplifies the structure of the heating device 10, and further reduces the production cost of the heating device 10.

[0060] In the spiral forward state, the fluid can not only maintain uniform heat exchange between each part of the fluid and the heating plate 200, but also ensure that it flows through the first flow channel 120 at a relatively fast speed, thereby improving the heating level of the heating device 10 as a whole and enhancing the heating performance of the heating device 10.

[0061] For example, along the extension direction of the first flow channel 120, the flow-disrupting structure 140 is inclined less than 90° relative to the centerline L of the first flow channel 120 (and may be inclined toward either side of the centerline L), as shown by angle α in FIG3 . Preferably, the angle α between the flow-disrupting structure 140 and the first flow channel 120 can be 80°, 70°, 60°, 50°, 40°, 30°, 20°, or 10°. Depending on the inclination of the flow-disrupting structure 140 relative to the centerline L of the first flow channel 120, the water flowing through the flow-disrupting structure 140 may experience different forward and reverse rotations.

[0062] In one example, referring to FIG. 1 and FIG. 2 , a flow guide space is provided in the housing 100 , and at least one first flow channel 120 is provided as a plurality of first flow channels 120 separated from each other in the flow guide space, and a flow spoiler structure 140 is provided in each of the plurality of first flow channels 120 .

[0063] For example, the plurality of first flow channels 120 may be arranged to extend in parallel or at different angles within the flow guiding space. Within the same flow range, the greater the number of first flow channels 120 , the better the disturbance effect of the flow-disturbing structure 140 .

[0064] In one example, the housing 100 defines an inlet 130 and an outlet 150 , and a cross-sectional area of ​​the inlet and / or the outlet perpendicular to the flow direction of the fluid is smaller than a cross-sectional area of ​​the at least one first flow channel or a sum of cross-sectional areas of the first flow channels.

[0065] The sum of the cross-sectional areas of the multiple first flow channels is set to be larger than the cross-sectional area of ​​the inlet / outlet, so that the flow rate of the fluid in the multiple first flow channels is slowed down compared to the flow rate of the fluid flowing through the inlet / outlet, further increasing the contact time between the fluid and the first flow channels. At the same time, the larger sum of the total cross-sectional areas is a larger fluid flow area, that is, the first flow channels occupy a larger space in the flow guide space, which also allows the fluid to have a larger contact area with the shell. The above features further enhance the heat exchange effect of the fluid. In this embodiment, the feature "the cross-sectional area of ​​the inlet and / or outlet is smaller than the cross-sectional area / the sum of the cross-sectional areas of at least one first flow channel" should be understood to include but not be limited to: the number of first flow channels is large and / or the cross-sectional area of ​​a single first flow channel is large.

[0066] In an exemplary embodiment, the shell 100 is provided with a plurality of bars 122 in the guide space to form a plurality of first flow channels 120, each bar 122 separates two adjacent first flow channels 120, wherein the heating plate 200 abuts against the plurality of bars 122, or a flow gap is provided between the heating plate 200 and the plurality of bars 122.

[0067] As shown in Figures 4 and 4A, the heating plate 200 abuts against the multiple bars 122, that is, one side surface of the heating plate 200 abuts against the top ends of the multiple bars 122, and there is no gap between the heating plate 200 and the multiple bars 122. When the space occupied by the first flow channel 120 is large enough, the desired fluid heat exchange efficiency is met. At this time, in order to ensure that a higher heating level is provided to the subsequent device, the fluid in the first flow channel 120 needs to have a faster flow speed. By setting the heating plate 200 to abut against the multiple bars 122 (that is, the fluids in the multiple first flow channels 120 are independent of each other, as shown in Figure 4A), the flow speed of the fluid in the first flow channel 120 is faster, while ensuring the heat exchange efficiency of the fluid, the heating level of the heating device 10 is further improved.

[0068] As shown in Figures 4 and 4B, a flow gap is provided between the heating plate 200 and the plurality of bars 122, that is, the heating plate 200 does not abut against the plurality of bars 122. When the space occupied by the plurality of first flow channels 120 is small due to design factors, in order to ensure that the fluid can achieve a good heat exchange level before flowing out of the outlet 150, it is necessary to increase the degree of disturbance of the fluid in the plurality of first flow channels 120 to achieve a higher level of fluid heat exchange. By arranging the heating plate 200 so that there is a flow gap between the heating plate 200 and the first flow channels 120 (that is, there is a mixing phenomenon of the fluid in the plurality of first flow channels 120, as shown in Figure 4B), the fluid in the plurality of first flow channels 120 can be further disturbed, thereby improving the heat exchange level of the fluid. The fluid with a higher degree of disturbance can also carry away more bubbles in the guide space.

[0069] In an exemplary embodiment, as shown in FIG5 , the housing 100 has a plurality of bars 122 formed in the flow guide space to form a plurality of first flow channels 120. Each of the plurality of first flow channels 120 is constructed to be symmetrical about a first direction or to be centrally symmetrical about itself. The housing 100 also has a plurality of guide plates formed in the flow guide space to form a plurality of second flow channels 160. An inlet 130 is formed on an inner wall (preferably a side wall) of the housing 100. The inlet 130 is oriented substantially perpendicular to the first direction. The plurality of guide plates include a first guide plate 162 extending between the inlet 130 and the plurality of bars 122. The end of the first guide plate 162 away from the plurality of bars 122 is arranged to gradually rise in the first direction along the direction of the inlet 130. That is, the length of the bars 122 increases as they are further away from the inlet 130.

[0070] Preferably, the first guide plates 162 are integrally formed with the housing 100 and arranged parallel to each other between the inlet 130 and the plurality of bars 122. Within the guide space, the distance from the heating plate 200 to the bottom of the housing 100 defines the maximum height of the first guide plates 162. Each guide plate separates two second flow channels 160, the width of which is preferably equal to the width of the first flow channel 120. One end of the second flow channel 160 is used to receive fluid from the inlet 130, and the other end faces the first flow channel 120 to guide the fluid toward the first flow channel 120. The multiple guide plates, which are arranged so that the direction of their inlet 130 is substantially perpendicular to the first direction, block the fluid that strikes the guide plates, causing it to flow into the corresponding second flow channels 160. The first guide plates 162 (indicated by the arrows in FIG. 5 ), which gradually rise in a first direction along the inlet 130 , allow the fluid to strike each guide plate without obstruction and then enter each second flow channel 160 , allowing the fluid to flow along the second flow channel 160 into the corresponding first flow channel 120 . The flow rate of the fluid from the outlet ends of the multiple first flow channels 120 can be adjusted.

[0071] The outlet 150 is formed on the inner wall of the shell 100, and the direction of the outlet 150 is basically perpendicular to the first direction. The multiple guide plates include a second guide plate 164 extending between the outlet 150 and the multiple bars 122. The end of the second guide plate 164 away from the multiple bars 122 is arranged to gradually rise in the first direction along the direction of the outlet 150 (as shown by the arrow in Figure 5), that is, the length of the bars 122 becomes longer as the distance away from the outlet 150 increases.

[0072] Preferably, the second guide plates 164 are integrally formed with the housing 100 and arranged parallel to each other between the outlet 150 and the plurality of bars 122. Within the guide space, the distance from the heating plate 200 to the bottom of the housing 100 defines the maximum height of the second guide plates 164. Each guide plate separates two second flow channels 160, the width of which is preferably equal to the width of the first flow channel 120. One end of the second flow channel 160 is used to receive fluid from the first flow channel 120, and the other end faces the outlet 150 to guide the fluid toward the outlet 150. When the fluid flows from the first flow channel 120 to the outlet 150 via the second flow channel 160 formed by the second guide plates 164, the second guide plates 164 gradually rise in the first direction along the direction of the outlet 150, so that the fluid does not become blocked when flowing out of the second flow channel 160 toward the outlet 150 and flows back into the first flow channel 120. In this example, the direction of the inlet 130 and the direction of the outlet 150 are both directed toward the interior of the guide space.

[0073] The first flow channel 120 symmetrical about the first direction or symmetrical about its own center can enable the inlet 130 and the outlet 150 to be used interchangeably.

[0074] The first flow channel 120 that is symmetrical about the first direction can be, for example, in the shape of "W", "M", "V", "U", "C", etc.; the first flow channel 120 that is centrally symmetrical about itself can be in the shape of "S", "N", "Z", etc.

[0075] In this embodiment, the term “substantially vertical” may, for example, mean that the orientation of the inlet 130 / outlet 150 is preferably 90° to the first direction.

[0076] In an exemplary embodiment, as shown in FIG5A , the ends of the first guide plates 162 away from the plurality of bars 122 are arranged to rise at equal intervals in a first direction along the direction of the inlet 130. That is, the bars 122 become longer as they move away from the outlet 150, and the absolute value L of the length difference between each bar 122 and its two sides is equal (as shown in FIG5A ). The first guide plates 162 that rise at equal intervals in the first direction along the direction of the inlet 130 ensure that the amount of fluid received by each guide surface from the inlet 130 is relatively uniform, that is, the amount of fluid introduced into the first flow channel 120 via the second flow channel 160 is also relatively uniform.

[0077] 5B , the ends of the second guide plates 164 away from the plurality of bars 122 are arranged to gradually and evenly rise in the first direction toward the outlet 150. When the positions of the inlet 130 and the outlet 150 need to be swapped due to actual installation reasons, the second guide plates 164 can also serve the same purpose as the first guide plates 162.

[0078] In an exemplary embodiment, as shown in Figure 5C, each of the first guide plates 162 includes a first portion 162a and a second portion 162b in sequence away from the multiple first flow channels 120, the first portion 162a of the first guide plate 162 extends along the first direction, and the second portion of the first guide plate 162 is constructed to be in an arc shape that bends toward the inlet 130.

[0079] Preferably, the first portion 162a extends along the first direction, the second portion 162b bends from the end of the first portion 162a away from the first flow channel 120 toward the inlet 130, each second portion 162b in the first guide plate 162 is equal, and the difference in length of the first guide plate 162 in the first direction is equal to the length of the second portion 162b.

[0080] The second portion 162b of the guide plate is constructed in an arc shape toward the inlet 130. When the second portion 162b is impacted by the fluid, its arc structure effectively avoids the occurrence of splashing, thereby ensuring uniform distribution of the multiple first flow channels 120.

[0081] As shown in Figure 5D, each of the second guide plates 164 includes a first portion 164a and a second portion 164b in sequence away from the multiple first flow channels 120. The first portion 164a of the second guide plate 164 extends along the first direction, and the second portion 164b of the second guide plate 164 is constructed to be curved toward the outlet 150.

[0082] Preferably, the first portion 164a extends along the first direction, the second portion 164b bends from the end of the first portion 164a away from the first flow channel 120 toward the outlet 150, each second portion 164b in the second guide plate 164 is equal, and the difference in length of the second guide plate 164 in the first direction is equal to the length of the second portion 164b.

[0083] For example, the height of the guide plates is equal to the height of the bars 122, and the width of the second flow channel 160 is equal to the width of the first flow channel 120. The positional relationship between the guide plates and the heating plate 200 is similar to the positional relationship and function between the bars 122 and the heating plate 200, and will not be further described here.

[0084] In some embodiments, the second portions of the arc-shaped structure may also extend into the inlet 130 / outlet 150 .

[0085] In an exemplary embodiment, as shown in FIG6 , the ends of the plurality of guide plates close to the plurality of bars 122 are respectively opposite to the ends of the plurality of bars 122 close to the plurality of guide plates. That is, the number of the first guide plates 162 is equal to the number of bars 122, which is equal to the number of the second guide plates. For example, the guide plates 330 of the second flow channel 160 can be integrally formed with the bars 122 of the first flow channel 120. Such an arrangement can quickly introduce the fluid from the second flow channel 160 into the first flow channel 120, and quickly introduce the fluid from the first flow channel 120 into the second flow channel 160. In the case of a large guide space, the fluid can quickly leave the guide space while achieving the expected heat exchange effect, which can provide a higher heating level for subsequent devices.

[0086] In another exemplary embodiment, as shown in FIG7 , the ends of the plurality of guide plates near the plurality of gratings 122 are staggered with the ends of the plurality of gratings 122 near the plurality of guide plates. For example, the first guide plate 162 of the second flow channel 160 can extend into the first flow channel 120 . This arrangement allows the fluids of two adjacent second flow channels 160 to be initially mixed upon entering the first flow channel 120 and before flowing through the flow-disturbing structure 140 ; ​​and allows the fluids of two adjacent first flow channels 120 to be finally mixed within the second flow channel 160 before flowing out of the outlet 150 .

[0087] In another exemplary embodiment, a transverse channel may be provided between the second flow channel and the first flow channel, which is configured to mix the fluid flow of the second flow channel. Before the fluid flow of the second flow channel enters the first flow channel and contacts the flow-disturbing structure, laminar flow still exists. The present disclosure provides a transverse channel between the second flow channel and the first flow channel, so that after the fluid passes through the transverse channel, it is mixed as a whole and flows into the first flow channel in a turbulent state; and before the fluid flows from the first flow channel into the second flow channel, it is mixed again and finally flows into the second flow channel again in a turbulent state.

[0088] In another embodiment, the present disclosure further provides a heating unit, comprising a heating device and the heating device according to the first aspect, wherein the heating device is used to heat a heating plate.

[0089] It should be understood that the term “including” and its variations used in the present disclosure are open inclusions, that is, “including but not limited to.” The term “one embodiment” means “at least one embodiment,” and the term “another embodiment” means “at least one additional embodiment.”

[0090] It should be noted that the various specific technical features (elements) described in the above specific embodiments can be combined in any appropriate manner without contradiction. In order to avoid unnecessary repetition, the present disclosure will not further describe various possible combinations.

[0091] The above are only specific embodiments of the present disclosure, but the scope of protection of the present disclosure is not limited thereto. Any changes or substitutions that can be conceived by any person skilled in the art within the technical scope disclosed in this disclosure should be included in the scope of protection of the present disclosure. Therefore, the scope of protection of the present disclosure should be based on the scope of protection of the claims.

Claims

1. A heating device, characterized in that: It comprises a heating plate and a shell having an inlet and an outlet, wherein the heating plate is arranged on one side of the shell to close the shell; At least one first flow channel is formed in the shell, and the fluid to be heated flows from the inlet to the outlet through the first flow channel, wherein a spoiler structure is arranged in the first flow channel, and the spoiler structure is constructed as a raised rib plate formed on the inner wall of the first flow channel, and the raised rib plate extends spirally along the extension direction of the first flow channel to disturb the flow of the fluid in the first flow channel.

2. The heating device according to claim 1, characterized in that A flow guiding space is arranged in the shell, the at least one first flow channel is arranged as a plurality of first flow channels separated from each other in the flow guiding space, and the flow disturbing structure is arranged in each of the plurality of first flow channels.

3. The heating device according to claim 2, characterized in that: The housing defines the inlet and the outlet, wherein a cross-sectional area of ​​the inlet and / or the outlet in a direction perpendicular to a flow direction of the fluid is smaller than a sum of cross-sectional areas of the plurality of first flow channels.

4. The heating device according to claim 2, characterized in that: The shell is formed with a plurality of bars in the guide space to form the plurality of first flow channels, each bar separating two adjacent first flow channels, wherein the heating plate abuts against the plurality of bars, or a flow gap is provided between the heating plate and the plurality of bars.

5. The heating device according to claim 4, characterized in that: Each of the plurality of first flow channels is constructed to be symmetrical about a first direction or to be centrally symmetrical about itself, and the housing is further formed with a plurality of guide plates in the guide space to form a plurality of second flow channels; The inlet is formed on the inner wall of the shell, the direction of the inlet is substantially perpendicular to the first direction, the plurality of guide plates include a first guide plate extending between the inlet and the plurality of bars, and an end of the first guide plate away from the plurality of bars is arranged to gradually rise in the first direction along the direction of the inlet, or gradually and evenly rise; and / or The outlet is formed on the inner wall of the shell, and the direction of the outlet is basically perpendicular to the first direction. The multiple guide plates include a second guide plate extending between the outlet and the multiple bars, and the end of the second guide plate away from the multiple bars is arranged to gradually rise in the first direction along the direction of the outlet, or gradually and evenly spaced.

6. The heating device according to claim 4, characterized in that: The shell has a plurality of bars formed in the flow guide space to form a plurality of first flow channels, each of the first flow channels is constructed to be symmetrical about a first direction or to be centrally symmetrical about itself, and the shell also has a plurality of guide plates formed in the flow guide space to form a plurality of second flow channels; The inlet is formed on the inner wall of the shell, the direction of the inlet is substantially perpendicular to the first direction, the plurality of guide plates include a first guide plate extending between the inlet and the plurality of bars, an end of the first guide plate away from the plurality of bars is arranged to gradually rise in the first direction along the direction of the inlet, and each of the first guide plates includes a first portion and a second portion in sequence away from the plurality of first flow channels, the first portion of the first guide plate extends along the first direction, and the second portion of the first guide plate is configured to be curved in an arc shape toward the inlet; and / or The outlet is formed on the inner wall of the shell, and the direction of the outlet is basically perpendicular to the first direction. The multiple guide plates include a second guide plate extending between the outlet and the multiple bars, and the end of the second guide plate away from the multiple bars is arranged to gradually rise in the first direction along the direction of the outlet, and each of the second guide plates includes a first part and a second part in sequence away from the multiple first flow channels, the first part of the second guide plate extends along the first direction, and the second part of the second guide plate is constructed to be curved in an arc toward the outlet.

7. The heating device according to claim 4, characterized in that Ends of the plurality of guide plates close to the plurality of grid bars are respectively opposite to ends of the plurality of grid bars close to the plurality of guide plates.

8. The heating device according to claim 4, characterized in that: Ends of the plurality of guide plates close to the plurality of grid bars are arranged alternately with ends of the plurality of grid bars close to the plurality of guide plates.

9. The heating device according to claim 4, characterized in that: A transverse channel is provided between the plurality of second flow channels and the plurality of first flow channels, and the transverse channel is configured to mix fluids flowing between the plurality of second flow channels and the plurality of first flow channels.

10. The heating device according to any one of claims 1 to 9, characterized in that: The first flow channel extends in a circuitous manner.

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