Steam exhaust structure and cooking equipment with steam function

Abstract

This invention relates to a steam exhaust structure and a cooking device with steaming function. The steam exhaust structure includes: a base plate; an air guide plate disposed on the base plate and forming an exhaust channel with the base plate, the exhaust channel including an air channel and a steam channel extending horizontally, the exhaust channel having a first mixing cross section, the air channel upstream of the first mixing cross section being independent of the steam channel, and the steam channel downstream of the first mixing cross section overlapping and communicating with the air channel vertically, with the overlapping portion of the air channel located below the steam channel; and a fan disposed on the base plate and connected to an air inlet upstream of the air channel, configured to drive air to flow along the air channel; by forming a stable layered structure of a lower high-speed airflow and an upper low-speed steamflow, a vertical height difference exists between the two, allowing steam and air to be fully mixed and discharged evenly, solving the problems of concentrated steam discharge and excessively high local temperatures.

Description

Technical Field

[0001] This invention relates to the technical field of steam exhaust in cooking equipment, and in particular to a steam exhaust structure and a cooking equipment with steaming function. Background Technology

[0002] Cooking equipment with steaming functions, such as steam ovens and steam ovens, generates a large amount of high-temperature steam inside the cavity during steaming mode. This steam needs to be expelled in a timely manner through a deflector assembly. Existing deflector assemblies for such cooking equipment typically adopt a single-duct structure, consisting of an upper mounting plate, a deflector plate, and a fan. The heat dissipation flow path and the steam exhaust flow path share the same channel.

[0003] However, the design of the heat dissipation flow path and steam outlet flow path in the existing solution is unreasonable. The high-temperature steam and the heat dissipation air are mixed directly in the air duct too early, and the fan blows at close range, which easily pushes the steam to one side, resulting in uneven distribution and excessive concentration of steam at the air outlet. The local exhaust temperature is too high, which poses a risk of burns to the cooking personnel. Summary of the Invention

[0004] Therefore, it is necessary to address the problem of concentrated steam emission in current cooking equipment with steaming function by providing a steam exhaust structure that can achieve uniform mixing of heat dissipation airflow and steam, as well as a cooking equipment with steaming function.

[0005] This application first provides a steam exhaust structure, comprising: a substrate; a guide plate disposed on the substrate and enclosing the substrate to form an exhaust channel, the exhaust channel including an air channel and a steam channel extending in a horizontal direction, the exhaust channel having a first mixing cross section, the air channel located upstream of the first mixing cross section being independent of the steam channel, the steam channel located downstream of the first mixing cross section overlapping and communicating with the air channel in a vertical direction, and the overlapping portion of the air channel being located below the steam channel; and a fan disposed on the substrate and connected to an air inlet upstream of the air channel, configured to drive air to flow along the air channel.

[0006] This configuration, in the overlapping and connected region downstream of the first mixing section, places the air channel in the lower layer and the steam channel in the upper layer, forming a stable stratified structure of high-speed airflow in the lower layer and low-speed steamflow in the upper layer. The fan is only connected to the air inlet of the air channel, and the cooling air it drives flows at high speed in the lower air channel. The steam channel is located above the air channel, and there is a vertical height difference between the two. This height difference confines the high-speed airflow generated by the fan within the lower air channel, preventing it from directly acting on the upper steam flow. This fundamentally avoids the problem of steam being blown to one side due to the fan being too close to the steam outlet, ensuring that the steam and air are fully mixed and discharged evenly. This solves the problems of concentrated steam discharge and excessively high local temperatures.

[0007] In one embodiment, the cross-sectional area of ​​the air channel located upstream of the first mixing section decreases downstream.

[0008] With this configuration, the cross-sectional area of ​​the air channel gradually decreases along the flow direction. According to the continuity equation, under the condition of constant flow, the decrease in cross-sectional area leads to a gradual increase in airflow velocity. Combined with Bernoulli's equation, the increase in airflow velocity causes its static pressure to gradually decrease, thereby forming a significant low-pressure zone near the first mixing section, providing sufficient pressure differential driving force for the steam in the upper steam channel of the siphon.

[0009] In one embodiment, the air channel located upstream of the first mixing section is a first air segment, and the height of the first air segment decreases downstream along a first direction; wherein, the first direction is parallel to the centerline direction of the first air segment.

[0010] With this configuration, the first air section achieves a sharp contraction of the cross-section by reducing the height of the upper wall, thereby increasing the airflow speed dramatically. Through this contraction design, the flow area of ​​high-speed airflow is controlled in the space near the bottom of the air guide plate, so that the airflow always flows close to the bottom surface.

[0011] In one embodiment, the air channel satisfies: 0.1H ≤ H1 ≤ 0.4H; Wherein, H is the initial height of the first air segment, and H1 is the height of the first air segment at the position of the first mixing section.

[0012] This configuration, by limiting the air passage to meet 0.1H≤H1≤0.4H, achieves a balance between the cross-sectional area reduction ratio and the flow channel resistance, ensuring both the heat dissipation performance requirements of the main air duct and the siphon effect of the mainstream high-speed air on the steam.

[0013] In one embodiment, the discharge channel further has a second mixing section located downstream of the first mixing section, and the air channel located downstream of the second mixing section intersects with the steam channel to form a mixing channel; The steam passage includes a first steam section located upstream of the second mixing section. The first steam section passes through the first mixing section, and the projection of its end along the vertical direction is located at the center of the air passage along the second direction. The exhaust passage satisfies: 0.4L≤L1≤0.65L. Wherein, the second direction is perpendicular to both the first direction and the vertical direction, L1 is the distance between the end of the first steam section and the air inlet along the first direction, and L is the total length of the air passage along the first direction.

[0014] With this configuration, by setting a second mixing section, the air channel and the steam channel are initially mixed at the first mixing section and then converge downstream of the second mixing section to form a mixing channel. A first steam section is set to pass through the first mixing section so that its end projection is located at the center of the air channel along the second direction. The exhaust channel is limited to satisfy 0.4L≤L1≤0.65L, so that the steam enters the mixing area from the center position and allows sufficient mixing stroke for the air and steam.

[0015] In one embodiment, the outflow channel satisfies: 30°≤α≤75°; Wherein, α is the angle between the centerline of the end of the first steam section and the centerline of the first air section.

[0016] This configuration, by limiting the exhaust channel to 30°≤α≤75°, controls the angle between the centerline of the end of the first steam section and the centerline of the first air section, allowing the steam to merge into the airflow at an appropriate angle, thus avoiding the steam from being concentrated on one side of the mixing initiation section.

[0017] In one embodiment, the external discharge channel satisfies: 0.35W ≤ W1 ≤ 0.65W; Wherein, W is the width of the outlet of the exhaust channel along the second direction, and W1 is the distance along the second direction between the end of the first steam section and the side of the outlet of the exhaust channel near the first steam section.

[0018] This configuration, by limiting the exhaust channel to meet 0.35W≤W1≤0.65W, and in conjunction with the α angle to limit the position of the end of the first steam section in the width direction, further ensures the uniformity of the lateral distribution of steam in the mixing section.

[0019] In one embodiment, the air channel further includes a second air section located downstream of the first mixing section, the height of the second air section remaining constant along the first direction, and the width of the second air section gradually increasing downstream along the first direction.

[0020] This configuration, by setting the second air section to keep its height constant along the first direction and its width gradually increasing downstream along the first direction, provides a stable flow space for the mixing of air and steam, and allows the mixed airflow to diffuse fully in the lateral space.

[0021] In one embodiment, the steam passage further includes a second steam section located downstream of the second mixing section, the second air section being directly opposite the outlet of the second steam section along the vertical direction and having the same width along the second direction.

[0022] By setting up the second steam section so that its outlet is directly opposite the outlet of the second air section in the vertical direction and has the same width in the second direction, the steam and air completely overlap at the outlet cross-section, thus achieving full mixing of the two.

[0023] In one embodiment, the height of the second steam section gradually decreases downstream along the first direction.

[0024] With this configuration, the height of the second steam section gradually decreases downstream along the first direction, causing the steam channel to gradually shrink and merge with the air channel, further improving the uniformity of steam distribution in the lateral space.

[0025] In one embodiment, the system includes a cooking chamber and the aforementioned steam exhaust structure, with the steam inlet upstream of the steam passage connected to the cooking chamber.

[0026] This design, by applying a steam exhaust structure to cooking equipment with a steam function, allows the high-temperature steam generated in the cooking chamber to be safely and evenly discharged, avoiding the risk of burns to users during use. Attached Figure Description

[0027] Figure 1 This is a three-dimensional schematic diagram of the steam exhaust structure of this application; Figure 2 for Figure 1 A three-dimensional schematic diagram of the central air guide plate from another angle; Figure 3 for Figure 1 A three-dimensional schematic diagram of the central air guide plate and the fan after they have been flipped over; Figure 4 for Figure 1 A schematic diagram of the central air guide plate viewed from the right. Figure 5 for Figure 1 A schematic diagram of the central air guide plate from a top-down perspective; Figure 6 for Figure 5 A schematic diagram of the first mixing section, the second mixing section, the first direction, and the second direction; Figure 7 This is a schematic diagram of the steam distribution characteristics of the steam exhaust structure of this application.

[0028] Reference numerals: 1. Substrate; 2. Air guide plate; 3. Fan; 10. Air passage; 10a. Air inlet; 11. First air section; 12. Second air section; 20. Steam passage; 20a. Steam inlet; 21. First steam section; 22. Second steam section; 30. Mixing passage. Detailed Implementation

[0029] To make the above-mentioned objects, features, and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of the present invention. However, the present invention can be practiced in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0030] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0031] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0032] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0033] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0034] It should be noted that when an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. When an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

[0035] Please combine Figure 1 , Figure 2 as well as Figure 3 As shown, this application first provides a steam exhaust structure, including a substrate 1 and a guide plate 2 disposed on the substrate 1. The substrate 1 and the guide plate 2 enclose an exhaust channel, which includes an air channel 10 extending horizontally and a steam channel 20. The exhaust channel has a first mixing section S1. The air channel 10 and the steam channel 20 upstream of the first mixing section S1 are independent of each other. The steam channel 20 downstream of the first mixing section S1 overlaps with and communicates with the air channel 10 vertically, and the overlapping portion of the air channel 10 is located below the steam channel 20. A fan 3 is disposed on the substrate 1 and connected to an air inlet 10a upstream of the air channel 10, configured to drive air to flow along the air channel 10.

[0036] In the overlapping and connected region downstream of the first mixing section S1, the air channel 10 is located in the lower layer and the steam channel 20 is located in the upper layer, forming a stable stratified structure of high-speed airflow in the lower layer and low-speed steamflow in the upper layer. The fan 3 is only connected to the air inlet 10a of the air channel 10, and the heat dissipation air driven by it flows at high speed in the lower air channel 10, while the steam channel 20 is located above the air channel 10. There is a vertical height difference between the two, which confines the high-speed airflow generated by the fan 3 within the lower air channel 10 and does not directly act on the upper steam flow, thus fundamentally avoiding the problem of the steam being blown to one side due to the fan being too close to the steam outlet.

[0037] The formation of the above-mentioned layered structure utilizes the physical properties of high-temperature steam. The density of high-temperature steam is greater than that of air at the same temperature. In a gravitational field, the denser steam flow is subjected to an upward buoyancy force and naturally gathers in the top space of the channel.

[0038] Therefore, in the vertically overlapping region downstream of the first mixing section S1, the steam always gathers in the upper space to form a steam channel 20 due to the buoyancy force, while the high-speed air forms an air channel 10 in the lower space under the drive of the fan 3. The two airflows naturally separate in the vertical direction, and a stable stratification state can be maintained without additional separation structures.

[0039] Furthermore, at the first mixing section S1, the high-speed airflow in the lower air passage 10 forms a significant low-pressure zone according to Bernoulli's principle. This low-pressure zone exerts a strong siphon effect on the low-speed steam flowing in the upper steam passage 20. Under this siphon effect, the steam is drawn into the lower airflow and thoroughly mixed with the high-speed air. Since the steam enters the airflow only after being siphoned, rather than being directly blown in by the fan, the lateral distribution of the steam is entirely determined by the uniformity of the siphon effect and is not affected by the non-uniformity of the flow field at the fan outlet.

[0040] When steam mixes with air, the overall temperature of the mixed airflow is reduced because the temperature of the air at the bottom is lower than that of the steam. Furthermore, the steam is evenly distributed in the horizontal space, which avoids concentrated steam discharge and ensures that the exhaust temperature of the air outlet is evenly distributed, thus eliminating the risk of burns.

[0041] In some embodiments, the air guide plate 2 adopts a one-piece molding design and can be made of high-temperature resistant plastic injection molding or metal sheet stamping. The upstream of the air passage 10 is directly connected to the fan 3, and the upstream of the steam passage 20 is connected to the exhaust pipe of the cooking chamber through the steam inlet 20a. The air passage 10 and the steam passage 20, located upstream of the first mixing section S1, are arranged in a V-shape and completely separated, and their flow channels converge at the first mixing section S1.

[0042] In another embodiment, the air guide plate 2 can also be assembled from multiple separate components, for example, by separately molding the lower wall of the air channel 10 and the upper wall of the steam channel 20 and then splicing them together. The fan 3 can be a high-speed DC centrifugal fan or an AC centrifugal fan, and its power can be matched and selected according to the heat dissipation requirements of the cooking equipment. The cross-sectional shape of the air channel 10 and the steam channel 20 is not limited to rectangle, but can also be trapezoidal or other conformal cross-sections, which is not limited in this invention.

[0043] Please combine Figure 2 , Figure 4 as well as Figure 6 As shown, in some embodiments, the cross-sectional area of ​​the air channel 10 located upstream of the first mixing section decreases downstream.

[0044] The cross-sectional area of ​​the air channel 10 gradually decreases along the flow direction. According to the continuity equation, under the condition of constant flow, the decrease in cross-sectional area leads to a gradual increase in airflow velocity. Combined with Bernoulli's equation, the increase in airflow velocity causes its static pressure to gradually decrease, thereby forming a significant low-pressure zone when approaching the first mixing section S1, providing sufficient pressure differential driving force for the steam in the upper steam channel 20 of the siphon.

[0045] Furthermore, please combine Figure 2 , Figure 4 as well as Figure 6As shown, in some embodiments, the air channel 10 located upstream of the first mixing section S1 is a first air segment 11. The height of the first air segment 11 decreases downstream along a first direction C1, wherein the first direction C1 is parallel to the centerline direction of the first air segment 11 (i.e., the flow direction of the first air segment 11).

[0046] The first air section 11 mainly achieves a sharp contraction of the cross-section by drastically reducing the height of the upper wall, thereby drastically increasing the airflow velocity and controlling the airflow area to be close to the bottom space.

[0047] Specifically, the upper wall extends downwards from the initial height H in the form of a continuous curved surface or folded surface until it reaches a height H1 at the first mixing section S1; through this contraction design, the flow area of ​​high-speed airflow is controlled in the space near the bottom of the air guide plate 2, so that the airflow always flows close to the bottom surface.

[0048] It is worth mentioning that since the air channel 10 and the steam channel 20 are independent of each other upstream of the first mixing section S1, that is, steam has not yet been introduced upstream of the first air section 11, the purpose of this design is to pre-control the airflow area in the space near the bottom layer so that when the air just comes into contact with the steam at the first mixing section S1, the high-speed airflow is in the lower layer and the steam is in the upper layer, thereby realizing the upper and lower layered flow and creating favorable initial flow field conditions for the formation of the subsequent siphon effect.

[0049] Furthermore, the effect of controlling the airflow at the bottom layer by the height reduction of the first air section 11 can also be combined with the design of the end of the first steam section 21 located at the center of the air channel 10 in the subsequent embodiment, so that when the steam is drawn into the bottom air flow from the upper center position, a natural confluence path is formed in the vertical direction, which helps to improve the uniformity of mixing.

[0050] It is understood that the height reduction of the first air section 11 can also be achieved by raising the lower wall surface upwards, or by simultaneously contracting the upper and lower walls. In one embodiment, the upper wall surface contracts using a rounded transition surface, resulting in a gentle change along the flow path, which helps reduce flow resistance. In another embodiment, the upper wall surface contracts using two folded surfaces: the first segment contracts rapidly at a large angle, and the second segment transitions gently to the position of the first mixing section S1 at a smaller angle.

[0051] Furthermore, please combine Figure 2 , Figure 4 as well as Figure 5As shown, in some embodiments, the initial height of the first air segment 11 is H, the height of the first air segment 11 at the first mixing section S1 is H1, and the air channel 10 satisfies 0.1H≤H1≤0.4H. That is, when other parameters remain unchanged, the cross-sectional shrinkage ratio of the cross-sectional area of ​​the first air segment 11 at the initial position to the cross-sectional area at the first mixing section S1 is between 10:1 and 2.5:1.

[0052] In this design, the air channel 10 achieves a sharp reduction in cross-sectional area through the contraction of its upper wall. According to the continuity equation, this reduction in cross-sectional area leads to a sharp increase in airflow velocity. Combined with Bernoulli's equation, the increased airflow velocity reduces its static pressure, thereby creating a sufficiently low-pressure zone at the first mixing section S1 to generate an effective siphon effect. The constraint of parameters 0.1H ≤ H1 ≤ 0.4H is a key design feature that balances the cross-sectional contraction ratio with the flow channel resistance.

[0053] If H1 is less than 0.1H, the cross-sectional shrinkage ratio is too large (shrinkage ratio greater than 10:1). In this case, the area difference between the first air section 11 and the outlet cross-section of the upstream fan 3 is too large. The rapid change in the cross-section along the flow path leads to a significant increase in the upstream flow channel resistance and a substantial reduction in the circulating air volume. The reduction in circulating air volume not only affects the heat dissipation performance requirements of the main air duct but also directly weakens the siphoning ability of the mainstream high-speed air to the steam, resulting in a decrease in the uniformity of steam distribution and failure to achieve the expected mixing effect.

[0054] If H1 is greater than 0.4H, the cross-sectional shrinkage ratio is insufficient (shrinkage ratio less than 2.5:1), resulting in insufficient acceleration of the mainstream air velocity. At this point, the air velocity at the first mixing section S1 is too low, leading to a higher static pressure. This results in insufficient pressure difference between the mainstream air and the steam, weakening the siphon effect. Under these circumstances, steam discharge is not smooth, and in severe cases, air may even flow back into the steam channel, preventing the steam from being effectively carried out and potentially causing it to flow back into the cooking cavity.

[0055] In one specific embodiment, H1 is set to 0.2H, i.e., the cross-sectional contraction ratio is 5:1. This value achieves a good balance between heat dissipation performance and siphon effect. In this embodiment, the upper wall of the first air section 11 contracts uniformly from height H to height H1. The length of the contracted section along the first direction C1 is moderate, ensuring that the friction resistance is within an acceptable range while also ensuring that the airflow velocity at the first mixing section S1 is sufficient to form an effective siphon. In another embodiment, H1 is set to 0.15H, which is suitable for high-power cooking equipment scenarios requiring a stronger siphon effect. In yet another embodiment, H1 is set to 0.35H, which is suitable for cooking equipment scenarios where heat dissipation is the primary function and steam emission is relatively small.

[0056] Furthermore, please combine Figure 2 , Figure 3 as well as Figure 5As shown, in some embodiments, the discharge channel also has a second mixing section located downstream of the first mixing section, and the air channel 10 located downstream of the second mixing section intersects with the steam channel 20 to form a mixing channel 30; The steam passage 20 includes a first steam section 21 located upstream of the second mixing section. The first steam section 21 passes through the first mixing section, and its end projection along the vertical direction is located at the center of the air passage 10 along the second direction C2. The second direction C2 (i.e., the width direction of the exhaust passage) is perpendicular to both the first direction C1 and the vertical direction. The exhaust passage satisfies 0.4L≤L1≤0.65L, where L1 is the distance between the end of the first steam section 21 and the air inlet 10a along the first direction C1, and L is the total length of the air passage 10 along the first direction C1.

[0057] The end of the first steam section 21 is located at the center of the width direction of the air channel 10, allowing steam to enter the mixing region from the center and laying the positional foundation for the uniform distribution of steam in the lateral space. Parameter L1 defines the position of the end of the first steam section 21 in the flow direction, and this parameter is closely related to the overall layout of the steam channel 20 and the air channel 10.

[0058] If L1 is less than 0.4L, then the length of the first air segment 11 in the flow direction is too short. This means that when the mainstream air channel 10 shrinks from a large-area, low-aspect-ratio cross-section to a small-area, high-aspect-ratio cross-section, the change in cross-section along the flow is too abrupt, increasing the resistance along the flow. This leads to a reduction in the airflow for heat dissipation, affecting the heat dissipation effect. At the same time, the excessively short shrinkage segment also results in insufficient acceleration of the airflow velocity, leading to uneven velocity distribution when it reaches the first mixing cross-section S1, affecting the consistency of the siphon effect.

[0059] If L1 is greater than 0.65L, the end of the first steam section 21 is too close to the outlet of the exhaust channel, leaving too short a mixing path for air and steam downstream. After entering the air channel 10 from the end of the first steam section 21, the steam needs sufficient flow distance to diffuse fully in the lateral space and mix evenly with the air. Insufficient mixing path will result in uneven lateral distribution of steam, increasing the maximum exhaust temperature at the outlet and posing a risk of burns.

[0060] In one specific embodiment, L1 is 0.5L, meaning that the end of the first steam section 21 is located slightly behind the midpoint of the air channel 10 along the flow direction. This position is the natural transition point after the first air section 11 has finished contracting. At this time, the airflow has completed acceleration and reached a stable high-speed state. After the steam enters from this central position, it can achieve uniform diffusion by utilizing the complete mixing stroke of the latter half of the exhaust channel.

[0061] Furthermore, the parameter limitation of H1 / H in the aforementioned embodiments provides the flow rate basis for the realization of the L1 / L parameter in this embodiment. Only when H1 / H is within a reasonable range can the air velocity at the first mixing section S1 match the mixing stroke defined by L1, forming a complete uniform mixing system. Specifically, H1 / H ensures that the air velocity at the first mixing section S1 is sufficiently high (forming an effective siphon), while L1 / L ensures that the steam has sufficient mixing stroke after entering from the center position (achieving uniform diffusion). Under the synergistic effect of both, after being siphoned into the airflow, the steam can fully diffuse to the entire channel width in the remaining mixing stroke.

[0062] Furthermore, please combine Figure 2 as well as Figure 5 As shown, in some embodiments, the exhaust channel satisfies 30°≤α≤75°, where α is the angle between the centerline of the end of the first steam section 21 and the centerline of the first air section 11.

[0063] The α angle controls the orientation angle of the last section of the first steam section 21, allowing the steam to merge into the airflow at an appropriate angle. The centerline of the end of the first steam section 21 is inclined relative to the first direction C1 (the main airflow direction), and this inclination angle directly affects the lateral position distribution of the steam when it enters the mixing region.

[0064] If α is less than 30°, during large-volume steam exhaust, the steam's lateral diffusion ability is insufficient due to the overly gentle slope at the end of the first steam section 21, which is close to the mainstream airflow direction. Furthermore, the relatively high steam velocity causes the steam to concentrate on the right side of the mixing initiation section (referring to the airflow direction within the air channel). The contraction of the downstream channel section prevents sufficient mixing of the right-concentrated steam with the air, resulting in uneven steam distribution and a higher exhaust temperature on the right side.

[0065] If α is greater than 75°, the last section of the first steam section 21 is too vertically oriented, resulting in excessively high steam velocity during large-volume steam exhaust. This causes the steam to concentrate on the left side of the mixing initiation section. Similarly, the downstream channel cannot fully mix the left-concentrated steam with the air, leading to uneven steam distribution and higher exhaust temperature on the left side.

[0066] In one specific embodiment, α is set to 55°. This value ensures that the end of the first steam section 21 extends towards the center of the air passage 10 at a moderate angle, so that the steam does not deviate to the left or right when entering the mixing region, resulting in the most uniform lateral distribution in the first mixing section S1. This α angle setting allows the end of the equal-section segment of the first steam section 21 to naturally transition to the central region of the air passage 10 in the width direction. In another embodiment, α is set to 45°, suitable for structures with a narrower steam passage 20. In yet another embodiment, α is set to 65°, suitable for structures where the steam passage 20 requires a longer transition section.

[0067] In addition, in the aforementioned embodiment, the first steam section 21 maintains a basically unchanged cross-sectional area and flow channel height upstream of the first mixing section S1, so that the flow rate of high-temperature steam is maintained at a low level. This low-speed characteristic, combined with the design of the α angle in this embodiment, ensures that the steam merges into the high-speed airflow at a controllable speed and angle.

[0068] Furthermore, please combine Figure 2 as well as Figure 5 As shown, in some embodiments, the air passage 10 further includes a second air section 12 located downstream of the first mixing section S1 and communicating with the first air section 11. The exhaust passage satisfies 0.35W ≤ W1 ≤ 0.65W, where W is the width of the outlet of the second air section 12 along the second direction C2, and W1 is the distance along the second direction between the end of the first steam section 21 and the side of the exhaust passage outlet near the first steam section 21.

[0069] In this embodiment, the parameter limitation of W1 / W works in conjunction with the α-angle parameter and the centering design of the end of the first steam segment 21 in the aforementioned embodiments. The centering design of the end of the first steam segment 21 defines the final target position (center) of the end in the width direction, the α-angle parameter defines the angular range of the end segment's direction (avoiding deviation to the left or right), and the parameter limitation of W1 / W defines the lateral landing point range of the end at that angle. The combination of these three factors ensures the uniform lateral distribution of steam in the first mixing section S1 from three dimensions: angle, position, and range.

[0070] The W1 / W parameter, along with the α angle, works synergistically to define the relative position of the end of the first steam section 21 in the width direction of the second air section 12 outlet. When the end of the first steam section 21 is located in the central region in the width direction, the steam diffuses equidistantly from this central position to both sides, resulting in the most uniform distribution of the mixed gas flow in the lateral space.

[0071] If W1 is less than 0.35W or α is less than 30°, the steam velocity is too high during large-volume steam exhaust, causing the steam to concentrate on the right side of the mixing initiation section. The downstream channel section contraction prevents sufficient mixing of steam and air, resulting in a higher exhaust temperature on the right side. If W1 is greater than 0.65W or α is greater than 75°, the steam concentrates on the left side of the mixing initiation section, leading to a higher exhaust temperature on the left side. Therefore, refer to... Figure 7 As shown, the mass fraction of H2O is the ratio of the mass of water vapor component to the total mass of the mixed gas flow. The parameters 0.35W≤W1≤0.65W and 30°≤α≤75° are satisfied simultaneously, which can more effectively ensure that the steam is laterally centered in the first mixing section S1 and achieve uniform coverage of steam in the width direction.

[0072] In one specific embodiment, W1 is set to 0.5W, meaning that the end of the first steam section 21 is located at the exact center of the outlet width of the second air section 12. This central arrangement ensures that the steam diffuses to both the left and right sides for a distance of 0.25W, achieving uniform coverage of the steam across the entire width direction within a limited mixing distance.

[0073] Furthermore, please combine Figure 2 as well as Figure 5 As shown, in some embodiments, the air channel 10 further includes a second air section 12 located downstream of the first mixing section. The height of the second air section 12 remains constant along the first direction C1, and the width of the second air section 12 gradually increases along the first direction C1 toward the side away from the first mixing section S1.

[0074] The second air section 12 maintains a constant height, providing a stable cross-sectional area and sufficient height for the mixing of air and steam. Within this space, the high-speed airflow from the first air section 11 mixes thoroughly with the steam from the first steam section 21. Simultaneously, the width of the second air section 12 gradually increases along the first direction C1, allowing the mixed airflow to diffuse fully in the lateral space and avoiding uneven distribution caused by concentrated airflow within a narrow channel.

[0075] The gradually increasing width of the second air section 12 is also adapted to the exhaust structure at the outlet. In one specific embodiment, the width of the second air section 12 at its downstream position is comparable to the width of the exhaust port, allowing the mixed airflow to be uniformly discharged to the outside through the exhaust port. The width gradually expands from the narrower dimension at the first mixing section S1 to the width of the exhaust port at the outlet, with a smooth and continuous expansion process, reducing flow losses and eddy current generation caused by abrupt changes in cross-section.

[0076] The structural design of the second air section 12 described in the previous embodiment, with its W1 / W parameter constraint, ensures that steam enters the mixing region from the center, while the structural design of the second air section 12 provides ample diffusion space for the mixed airflow diffusing from the center to both sides through a channel structure with gradually increasing width. The combination of these two factors allows the steam, after being siphoned into the airflow, to naturally and uniformly distribute across the entire width of the gradually expanding channel in the second air section 12.

[0077] It is understood that the width of the second air section 12 can be increased not only linearly, but also exponentially or by a circular curve. In one embodiment, the width of the second air section 12 increases linearly, which simplifies the manufacturing process and facilitates integral molding. In another embodiment, the width of the second air section 12 increases by a circular curve, resulting in a slower expansion rate in the initial mixing region, providing a relatively stable flow environment for the initial mixing of steam and air, and a faster expansion rate near the outlet region, allowing the mixed airflow to diffuse sufficiently before discharge.

[0078] Furthermore, please combine Figure 2 , Figure 3 as well as Figure 5 As shown, in some embodiments, the steam passage 20 further includes a second steam section 22 located downstream of the second mixing section. The outlets of the second air section 12 and the second steam section 22 are directly opposite each other in the vertical direction and have the same width in the second direction C2.

[0079] In this design, the outlets of the second air section 12 and the second steam section 22 are vertically aligned, meaning that steam exiting the second steam section 22 directly enters the airflow region of the second air section 12, forming a complete vertical overlap. Both sections have the same width along the second direction C2, ensuring complete lateral correspondence between the steam outlet and the air outlet, eliminating any blind spots where steam cannot be covered by air. This structural design allows for complete overlap of steam and air at the outlet cross-section, creating optimal spatial conditions for their thorough mixing.

[0080] It should be noted that in this application, the second air section 12 is located downstream of the second mixing section S2 and forms a mixing channel 30 with the second steam section 22, and the air and steam are fully mixed in the mixing channel 30; that is, the second air section 12 and the second steam section 22 do not limit the internal airflow type, and the air-steam mixed airflow actually flows in the second air section 12 and the second steam section 22 of the mixing channel 30.

[0081] In one specific embodiment, the outlet cross-section of the second steam section 22 and the corresponding cross-section of the second air section 12 are both rectangular, and their widths and positions in the second direction C2 are completely identical. When steam exits from the second steam section 22, its entire width is covered by the high-speed airflow of the second air section 12 below. The steam is immediately entrained in the airflow upon exit, and there is no steam leakage from the edges. This structure ensures that the mixed airflow achieves initial mixing before leaving the exhaust channel, and further diffusion after exit makes the temperature distribution more uniform.

[0082] Furthermore, please combine Figure 2 and Figure 4 As shown, in some embodiments, the height of the second steam section 22 gradually decreases downstream along the first direction C1.

[0083] The second steam section 22 gradually decreases in height while gradually expanding in width, eventually merging with the second air section 12. This gradual change in cross-section makes the steam distribution in the lateral space more uniform, avoiding flow losses, eddy currents, and uneven distribution caused by abrupt changes in cross-section. The cross-section of the steam channel 20 transitions from the constant cross-section of the first steam section 21 to the gradually changing cross-section of the second steam section 22. The steam velocity increases moderately as the cross-section decreases, which facilitates the diffusion of steam into the lateral space.

[0084] In one specific embodiment, the height of the second steam section 22 decreases linearly. Starting from the connection point with the first steam section 21, the height of the second steam section 22 decreases uniformly along a first direction C1 until it merges with the upper wall of the second air section 12 at its downstream end. This linearly decreasing height design keeps the rate of change of the cross-sectional area of ​​the steam channel 20 constant, ensuring stable and controllable steam flow within the channel. Simultaneously, the width of the second steam section 22 can gradually increase, resulting in a smooth change in the overall cross-sectional area of ​​the steam channel 20 despite the decreasing height, preventing a sudden increase in steam velocity and flow instability caused by a rapid reduction in cross-section.

[0085] In another embodiment, the height of the second steam section 22 decreases in a quadratic curve manner. The height decreases slowly in the initial stage of mixing to provide sufficient space for the initial mixing of steam and air. The height decreases more rapidly near the end, so that the steam channel 20 can be smoothly integrated into the air channel 10.

[0086] The design of the second steam section 22 with decreasing height, combined with the design of the second air section 12 with constant height in the previous embodiment, forms a complementary structure in the vertical direction. This ensures that the air channel 10 maintains sufficient height space in the downstream region, while the steam channel 20 gradually shrinks and merges into this space. The height difference between the two is greatest at the first mixing section S1 (which is beneficial for siphoning) and tends to zero at the downstream end (which is beneficial for fusion), forming a natural vertical transition.

[0087] The present invention also provides a cooking device with a steaming function, including a cooking chamber and the aforementioned steam exhaust structure. The steam inlet 20a upstream of the steam channel 20 is connected to the cooking chamber.

[0088] In one specific embodiment, the cooking device is a steam oven. During steam mode, a large amount of high-temperature steam is generated inside the cavity of the steam oven. This high-temperature steam enters the steam channel 20 through the exhaust pipe and steam inlet 20a at the top of the cooking cavity. Under the action of the steam exhaust structure, the high-temperature steam mixes evenly with the cooling air, resulting in a lower temperature and more even distribution. Finally, it is discharged outside the device through the outlet of the exhaust channel.

[0089] By organically integrating the steam exhaust structure with the cooking chamber, the high-temperature steam generated in the cooking chamber can be safely and evenly discharged. Furthermore, the steam exhaust structure, through the combined effects of the aforementioned dual-duct structure, parameter limitations, and geometric design, ensures that the steam remains in a controllable flow state throughout the entire process from generation to final discharge, preventing issues such as concentrated emissions and excessively high local temperatures.

[0090] In another embodiment, the cooking device is a steam oven. Steam ovens primarily use steam heating for cooking, generating a large amount of steam, thus requiring a higher exhaust capacity from the steam venting structure. Using the steam venting structure of this invention, by rationally selecting the parameters H1 / H, L1 / L, α, and W1 / W, the requirement for uniform mixing during large-volume steam exhaust can be met. In yet another embodiment, the cooking device is a microwave oven with steam cooking function. Since the amount of steam generated is relatively small, the parameter range can be appropriately relaxed to simplify the structural design.

[0091] It is understandable that the values ​​of the parameters in the above steam exhaust structure can be adjusted according to the specific type of cooking equipment and the amount of steam generated. For large-capacity commercial steam ovens, a combination of H1 = 0.15H, L1 = 0.55L, α = 50°, and W1 = 0.5W can be selected to obtain a stronger siphon effect and a longer mixing stroke. For small household steam ovens, a combination of H1 = 0.3H, L1 = 0.45L, α = 60°, and W1 = 0.5W can be selected to achieve a good mixing effect within a limited space.

[0092] The aforementioned cooking equipment with steaming function can be controlled by a voice module. It is equipped with a controller, a voice receiving module, and a voice parsing module. The voice receiving module receives user commands, and the voice parsing module parses the commands. Based on the parsed commands, the controller controls the cooking equipment to perform corresponding operations, thereby realizing intelligent control of the cooking equipment and improving the user experience.

[0093] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0094] The embodiments described above are merely illustrative of several implementations of the present invention, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the invention patent. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these all fall within the protection scope of the present invention. Therefore, the protection scope of this invention patent should be determined by the appended claims.

Claims

1. A steam exhaust structure, characterized in that, include: substrate(1); A guide plate (2) is disposed on the substrate (1) and surrounds the substrate (1) to form an exhaust channel. The exhaust channel includes an air channel (10) extending in a horizontal direction and a steam channel (20). The exhaust channel has a first mixing cross section. The air channel (10) located upstream of the first mixing cross section is independent of the steam channel (20). The steam channel (20) located downstream of the first mixing cross section overlaps with and communicates with the air channel (10) in a vertical direction, and the overlapping portion of the air channel (10) is located below the steam channel (20). A fan (3) is disposed on the substrate (1) and connected to an air inlet (10a) upstream of the air channel (10), and is configured to drive air to flow along the air channel (10).

2. The steam exhaust structure according to claim 1, characterized in that, The cross-sectional area of ​​the air channel (10) located upstream of the first mixing section decreases downstream.

3. The steam exhaust structure according to claim 2, characterized in that, The air channel (10) located upstream of the first mixing section is the first air section (11), and the height of the first air section (11) decreases downstream along the first direction; The first direction is parallel to the centerline direction of the first air segment (11).

4. The steam exhaust structure according to claim 3, characterized in that, The air channel (10) satisfies: 0.1H≤H1≤0.4H; Wherein, H is the initial height of the first air section (11), and H1 is the height of the first air section (11) at the first mixing section position.

5. The steam exhaust structure according to claim 2, characterized in that, The discharge channel also has a second mixing section located downstream of the first mixing section. The air channel (10) located downstream of the second mixing section intersects with the steam channel (20) to form a mixing channel (30).

6. The steam exhaust structure according to claim 5, characterized in that, The steam channel (20) includes a first steam section (21) located upstream of the second mixing section. The first steam section (21) passes through the first mixing section, and the projection of its end along the vertical direction is located at the center of the air channel (10) along the second direction. The exhaust channel satisfies: 0.4L≤L1≤0.65L. Wherein, the first direction is parallel to the centerline direction of the first air section (11), the first air section (11) is the part of the air channel (10) located upstream of the first mixing section, the second direction is perpendicular to both the first direction and the vertical direction, L1 is the distance between the end of the first steam section (21) and the air inlet (10a) along the first direction, and L is the total length of the air channel (10) along the first direction.

7. The steam exhaust structure according to claim 6, characterized in that, The external discharge channel satisfies: 30°≤α≤75°; Wherein, α is the angle between the centerline of the end of the first steam section (21) and the centerline of the first air section (11).

8. The steam exhaust structure according to claim 7, characterized in that, The external discharge channel satisfies: 0.35W ≤ W1 ≤ 0.65W; Wherein, W is the width of the outlet of the exhaust channel along the second direction, and W1 is the distance along the second direction between the end of the first steam section (21) and the side of the outlet of the exhaust channel near the first steam section (21).

9. The steam exhaust structure according to claim 8, characterized in that, The air channel (10) further includes a second air section (12) located downstream of the first mixing section. The height of the second air section (12) remains constant along the first direction, and the width of the second air section (12) gradually increases downstream along the first direction.

10. The steam exhaust structure according to claim 9, characterized in that, The steam passage (20) further includes a second steam section (22) located downstream of the second mixing section, wherein the outlets of the second air section (12) and the second steam section (22) are directly opposite each other in the vertical direction and have the same width in the second direction.

11. The steam exhaust structure according to claim 10, characterized in that, The height of the second steam section (22) gradually decreases downstream along the first direction.

12. A cooking device with a steaming function, characterized in that, It includes a cooking chamber and a steam exhaust structure as described in any one of claims 1 to 11, wherein the steam inlet (20a) upstream of the steam passage (20) is connected to the cooking chamber.

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