Condenser of refrigeration extractor hood and refrigeration extractor hood

Abstract

The utility model discloses a condenser of a refrigeration range hood. The condenser comprises a refrigerant channel, the condenser is characterized in that the condenser further comprises a main body capable of conducting heat, the refrigerant channel is arranged on the main body, the main body comprises a first part and a second part, the first part is in a pipeline shape and defines a smoke exhaust channel for oil smoke to pass through, and the second part is arranged in a space defined by the first part. The second part is arranged on the main body and is in direct contact or indirect contact with the first part to form a heat conduction path, seen from the end face of the main body, the sectional area of a smoke exhaust channel defined by the first part is S1, the sectional area of the second part is S2, and S2 is smaller than or equal to 0.005 S1.

Description

Technical Field

[0001] The utility model relates to a refrigeration device, in particular to a condenser of a refrigeration range hood and a refrigeration range hood using the condenser. Background Art

[0002] With the improvement of material living standards, people have higher and higher requirements for kitchen environment. People need to use stoves during cooking, which will generate a lot of heat in the kitchen, causing the temperature of the entire space to rise and the comfort of the environment to decrease. At present, most families use temporary fans to solve this problem. However, this method is not only inconvenient, but also occupies kitchen area.

[0003] For this purpose, a range hood with a refrigeration function has been disclosed in the prior art, which can blow out cold air from the housing of the range hood to cool down the kitchen. For example, a Chinese patent with application number 201810525673.7 discloses an air-conditioning range hood, in which the fume assembly of the air-conditioning range hood includes an oil fume channel; the air-conditioning assembly includes a condenser assembly, and the condenser assembly includes a condensation air inlet and a condensation air outlet, the condensation air outlet is connected to the oil fume channel, and the condensation air inlet is independent of the oil fume channel. However, the arrangement of this condenser uses the main fan for oil fume extraction to dissipate heat, which reduces the amount of oil fume sucked and exhausted, affecting the oil fume extraction effect.

[0004] There is also a kitchen air conditioner disclosed in a Chinese patent with application number 202110029969.1, which includes an air conditioning component and a range hood component. The air conditioning component includes a compressor, a condenser, a throttling element, and an evaporator. The range hood component includes an exhaust duct and a exhaust fan in the exhaust duct. The condenser is arranged around the outer wall of the exhaust duct.

[0005] This type of kitchen air conditioner can use oil smoke to dissipate heat from the condenser without additional power. However, since the condenser is wrapped outside the exhaust pipe, it is usually not guaranteed that the condenser can be completely close to the exhaust pipe when wrapped, resulting in an air gap layer; and the oil smoke needs to pass through the heat-conducting smoke pipe to exchange heat with the condenser wall, and the long heat exchange path will lead to low heat exchange efficiency. Utility Model Content

[0006] The first technical problem to be solved by the present invention is to provide a condenser for a refrigeration range hood in view of the deficiencies in the above-mentioned prior art, which can improve the heat exchange efficiency without affecting the exhaust effect of oil fumes.

[0007] The second technical problem to be solved by the utility model is to provide a refrigeration range hood using the above condenser.

[0008] The technical solution adopted by the utility model to solve the first technical problem mentioned above is: a condenser of a refrigeration range hood, including a refrigerant channel; characterized in that: the condenser also includes a main body capable of conducting heat, the refrigerant channel is arranged on the main body, the main body includes a first part and a second part, the first part is in a pipe shape and forms an exhaust channel for oil smoke to pass through, the second part is arranged in the space surrounded by the first part, and forms a heat conduction path with the first part through direct or indirect contact, and viewed from the end face of the main body, the cross-sectional area of ​​the exhaust channel surrounded by the first part is S1, and the cross-sectional area of ​​the second part is S2, S2≤0.005S1.

[0009] By making the main body of the condenser include a first part in the shape of a pipe and a second part located in the space surrounded by the first part, the area in contact with the oil smoke is larger under the same volume, which can further improve the overall heat exchange efficiency; in addition, since the central wind speed of the condenser is high, the heat can be transferred to the center through the setting of the second part, and the high wind speed at the center position can be used to quickly take away the heat, which can further improve the overall heat exchange efficiency; and the cross-sectional area of ​​the second part is much smaller than the cross-sectional area of ​​the smoke exhaust channel, so as to avoid the second part from causing greater resistance to the discharge of oil smoke due to occupying a larger proportion of the smoke exhaust channel, thereby ensuring that the oil smoke can still be discharged smoothly.

[0010] Furthermore, the first part includes a first inner wall surface in contact with the oil fume and a first outer wall surface not in contact with the oil fume, and the second part includes a second inner wall surface and a second outer wall surface both in contact with the oil fume, and the first inner wall surface and the first outer wall surface of the first part and the second inner wall surface and the second outer wall surface of the second part all constitute heat dissipation surfaces. Therefore, by making each wall surface of the first part and the second part constitute a heat dissipation surface, the main body is utilized to the greatest extent for heat dissipation, thereby ensuring that the heat dissipation effect is maximized.

[0011] Furthermore, the area of ​​the first inner wall surface of the first part is S 11 , the area of ​​the first outer wall of the first part is S 12 , the area of ​​the second inner wall of the second part is S 21 , the area of ​​the second outer wall of the second part is S 22 , and satisfy S 21 +S 22 ≥0.6(S 11 +S 12 ), so that the second part has enough heat dissipation area to make full use of the high central wind speed to improve the heat dissipation efficiency. The setting of the second part also plays a role in sharing the heat of the first part, reducing the impact of the heat radiation of the first part on other components in the range hood.

[0012] According to one aspect of the utility model, a gap is formed inside the wall portion of only the first part of the main body, and the gap directly constitutes the refrigerant channel.

[0013] According to another aspect of the utility model, refrigerant channels are provided on both the first part and the second part, the volume of the refrigerant channel on the first part is V1, the volume of the refrigerant channel on the second part is V2, and V2≥V1 is satisfied, so that when the refrigerant flows into the refrigerant channel of the second part, a larger amount of refrigerant can utilize the high central wind speed to improve the heat dissipation efficiency.

[0014] Further, according to one aspect of the utility model, in order to reduce the resistance to the flow of oil smoke, reduce the generation of eddy currents, and increase the contact path with the oil smoke, part of the refrigerant channel is directly formed by the gap inside the wall of the main body, and the position corresponding to the refrigerant channel of the main body is formed with a raised ridge, and the refrigerant channel has at least a transverse channel extending laterally. On the cross section of the refrigerant channel, the outer contour of the ridge corresponding to the transverse channel has a lowest point A on the side facing the oil smoke, and the vertical line passing through the lowest point A is the Y-axis. The point on the outer contour with the largest horizontal distance from the Y-axis is B, and the horizontal line passing through point B is the X-axis. The intersection of the X-axis and the Y-axis is the origin, the distance between point A and the origin is a, the distance between point B and the origin is b, and the angle formed by the straight line connecting point A and point B and the Y-axis is α, and α is less than 45°.

[0015] According to one aspect of the utility model, the second part is formed by the inward extension of the wall surface of the first part, so that the first part and the second part are in direct contact with each other to dissipate heat, the heat transfer path is short, and the heat transfer efficiency is high.

[0016] Preferably, the second part has n+1 winding layers, n is a natural number ≥ 3, and the distance between the innermost layer located at or near the center and the adjacent layer is d 11 , the distance between the second layer near the center and the adjacent layer outside is d 12 , and so on, the distance between the outermost layer and its adjacent layer is d 1n , each spacing value is within the range of 5 mm to 200 mm; or, the second part has n+1 winding layers, n=2, and the spacing between the innermost layer located at or near the center and the adjacent layer is d 11 , the distance between the second layer near the center and the adjacent layer outside is d 12 , each spacing value is within the range of 5mm to 200mm, so that the oil smoke can pass smoothly.

[0017] The technical solution adopted by the utility model to solve the above-mentioned second technical problem is: a refrigeration range hood, including a fume suction component and a refrigeration component, the fume suction component including a first shell and a fan arranged in the first shell; it is characterized in that: the refrigeration component includes a condenser as described above, the condenser is connected to the first shell and is arranged at the air outlet of the fan.

[0018] Furthermore, the first part of the main body is a vertically arranged rectangular parallelepiped, and the bottom of the first part of the main body is formed with an outwardly bent flange, and the flange is fixed to the top of the first shell. The main body can be conveniently arranged through the first part of the rectangular parallelepiped on the outside of the main body, and in particular, the main body can be directly arranged at the air outlet of the fan, so that the heat of the main body can be transferred to the first shell of the range fumes suction assembly with a larger heat dissipation area and the metal connection parts such as the volute of the fan by heat conduction, which is equivalent to a wider heat transfer area under the action of airflow.

[0019] Furthermore, the refrigerant channel of the condenser includes a vertical channel and a transverse channel. The transverse channel is bent relative to the vertical channel. By increasing the bends, it is beneficial to extend the pipe path and increase the heat exchange capacity. The setting of the vertical channel can make the heat exchange area larger when the oil smoke flows through, and the heat exchange efficiency is good. In addition, the vertical channel has a good guiding effect on the oil and avoids the accumulation of oil on the condenser.

[0020] Preferably, in order to further increase the heat exchange capacity, the main body of the condenser is raised at a position corresponding to the refrigerant channel to form a ridge, and on a cross section perpendicular to the extension direction of the refrigerant channel, the outer contour of the ridge is consistent with the contour shape of the refrigerant channel, and the ratio of the total length of the vertical channel to the total length of the transverse channel is not less than 1.1.

[0021] Compared with the prior art, the utility model has the following advantages: the gap inside the main wall of the condenser directly constitutes a refrigerant channel, so that the refrigerant directly contacts the main body for heat transfer, and the heat is dissipated by the oil smoke passing through the space surrounded by the pipe. The heat transfer path between the refrigerant channel and the heat-dissipating oil smoke is short, so that the refrigerant flowing inside the condenser tube wall can be fully dissipated, thereby improving the refrigeration effect of the refrigeration component; and the main body of the condenser includes a first part in the shape of a pipe and a second part curled inward by the wall surface of the first part. Under the same volume, it has a larger area in contact with the oil smoke, which can further improve the overall heat exchange efficiency; in addition, since the central wind speed of the condenser is high, the heat can be transferred to the center through the setting of the second part, and the high wind speed at the center position can be used to quickly take away the heat, which can further improve the overall heat exchange efficiency; and the cross-sectional area of ​​the second part is much smaller than the cross-sectional area of ​​the smoke exhaust channel, so as to avoid the second part from occupying a larger proportion of the smoke exhaust channel and causing greater resistance to the discharge of the oil smoke, thereby ensuring that the oil smoke can still be discharged smoothly. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Figure 1 A schematic diagram of a range hood according to a first embodiment of the utility model;

[0023] Figure 2 This is a schematic diagram of the exploded structure of the range hood of the first embodiment of the utility model;

[0024] Figure 3 It is a schematic diagram of the range hood of the first embodiment of the utility model, in which the range hood assembly and the refrigeration assembly respectively hide part of the housing;

[0025] Figure 4 It is a cross-sectional view of a refrigeration assembly of a range hood according to the first embodiment of the utility model;

[0026] Figure 5 A schematic diagram of a condenser of a refrigeration assembly of a range hood according to a first embodiment of the utility model (with the flange hidden);

[0027] Figure 6 A top view of a condenser of a refrigeration assembly of a range hood according to a first embodiment of the utility model;

[0028] Figure 7 It is a schematic diagram of the expansion of the condenser of the refrigeration assembly of the range hood according to the first embodiment of the utility model;

[0029] Figure 8 for Figure 7 AA section view;

[0030] Fig. 9 Schematic diagram of velocity field distribution of different refrigerant channel cross sections;

[0031] Fig.10 It is a partial cross-sectional view of the main body of the condenser of the refrigeration assembly of the range hood according to the first embodiment of the utility model (only the outer contour is shown);

[0032] Fig.11 A bottom view of an alternative embodiment of a condenser of a refrigeration assembly of a range hood of the utility model;

[0033] Fig.12 A schematic diagram of a condenser of a refrigeration assembly of a range hood according to a second embodiment of the utility model;

[0034] Fig.13 A cross-sectional view of a condenser of a refrigeration assembly of a range hood according to a second embodiment of the utility model;

[0035] Fig.14 for Fig.13 A schematic diagram of the partial enlargement of Ⅰ. DETAILED DESCRIPTION

[0036] Embodiments of the present utility model are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals represent the same or similar elements or elements with the same or similar functions.

[0037] In the description of the present utility model, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate the orientation or position relationship based on the orientation or position relationship shown in the drawings, which is only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Since the embodiments disclosed in the present utility model can be set in different directions, these terms indicating directions are only for illustration and should not be regarded as limitations. For example, "up" and "down" are not necessarily limited to directions opposite to or consistent with the direction of gravity. In addition, the features defined as "first" and "second" may explicitly or implicitly include one or more of such features.

[0038] Embodiment 1

[0039] See also Figure 1 to Figure 6 A refrigeration range hood includes a range hood assembly and a refrigeration assembly, wherein the range hood assembly includes a first shell 11 and a fan 12 disposed in the first shell 11. In this embodiment, the range hood assembly is in the form of a commonly used side-suction range hood. Alternatively, it can be an existing top-suction, low-suction, etc. The first shell 11 can be a combination of one or more shells.

[0040] The oil fume suction component and the refrigeration component constitute independent modules respectively. When installed, the refrigeration component is mounted on the oil fume suction component, so that the refrigeration component does not occupy the left and right sides of the first shell 11 of the oil fume suction component, which can avoid the fan frame (part of the first shell 11) used to set the fan 12 from being offset and affecting its own oil fume suction effect. Moreover, the two modules are installed independently, which can meet the needs of both new decoration users and old users who are changing their decoration.

[0041] The refrigeration assembly includes a second shell 21, a compressor 22, an evaporator 23, a condenser 24 and a cooling fan 25, wherein the second shell 21 is arranged on the first shell 11, wherein the compressor 22, the evaporator 23, the condenser 24 and the cooling fan 25 can be arranged in the second shell 21, and a refrigerant passage is formed between the compressor 22, the evaporator 23 and the condenser 24. The working principle of the refrigeration assembly is the same as the prior art.

[0042] The refrigeration range hood further includes an outer cover 4, which is arranged on the outside of the refrigeration assembly and part of the first shell 11, but may not include the top of the refrigeration assembly, the first shell 11 and the rear side of the refrigeration assembly. A cold air outlet 41 is provided on the front side of the outer cover 4, such as near the top. The evaporator 23 can be arranged near the cold air outlet 41. The cold air after heat exchange in the evaporator 23 is blown out from the cold air outlet 41 to the kitchen through the cooling fan 25 to provide a comfortable cooking environment temperature for the user. The refrigeration assembly also includes an air outlet assembly 26, which is arranged at the cold air outlet 41. The air outlet of the cooling fan 25 can be directly or indirectly connected to the air outlet assembly 26. The air outlet assembly 26 is similar to the air outlet assembly of the air conditioner, and a guide vane can be provided to change the direction of the air outlet. An air inlet 211 is provided on the top of the second shell 21 to replenish air (room temperature air) into the second shell 21 to exchange heat with the evaporator 23. A filter module can be provided at the air inlet 211.

[0043] The condenser 24 includes a main body 241 and a refrigerant channel 242. The main body 241 is in the shape of a hollow pipe, and the refrigerant channel 242 is formed inside the wall of the main body 241. The main body 241 includes two layers of heat conducting plates 2411, and the refrigerant channel 242 is formed between the two layers of heat conducting plates 2411. The two layers of heat conducting plates 2411 have a gap only at the position where the refrigerant channel 242 is formed, that is, the gap constitutes the refrigerant channel 242, and the other parts are all fitted (the gaps in the parts outside the refrigerant channel 242 caused by processing problems, such as bubbles, should be regarded as a situation without gaps). Optionally, the heat conducting plate 2411 is a metal plate, such as an aluminum plate, and two pieces of aluminum plates are hot-rolled and pressed, and the above-mentioned refrigerant channel 242 is formed between the two pieces of aluminum plates by processes such as inflation or wire cutting (inflation process is used in this embodiment), and then the whole is rolled into a desired shape. After hot rolling, the refrigerant in the refrigerant channel 242 can withstand a pressure of up to 2.3MPa, and there is zero gap contact between the refrigerant and the heat conducting plate 2411, and the heat exchange efficiency is extremely high, so the surface temperature of the condenser under natural conditions is not higher than 50°C. In other words, the refrigerant channel 242 does not need to be formed by laying additional pipes, but is directly formed between the two layers of heat conducting plates 2411. The refrigerant in the refrigerant channel 242 directly contacts the opposite side walls of the two layers of heat conducting plates 2411, and the side wall of the inner layer heat conducting plate 2411 away from the outer layer heat conducting plate 2411 directly contacts the oil smoke, and there is less heat transfer medium between the oil smoke and the refrigerant, and the heat transfer efficiency is high. The condenser 24 formed in this way, because the refrigerant channel 242 is formed inside the wall of the main body 241, and the heat conducting plate 2411 of the main body 241 is a plate of equal thickness, the main body 241 is convex at the position corresponding to the refrigerant channel 242, thereby forming a convex ridge 2417, and on the cross section perpendicular to the extension direction of the refrigerant channel 242 (the cross section is the plane where the cross section of the refrigerant channel 242 is located), the outer contour of the ridge 2417 is consistent with the contour shape of the refrigerant channel 242. In the fin type commonly used in existing air conditioners or the winding type described in the background technology, the refrigerant and the heat conducting material cannot be completely matched without gaps, so the heat transfer is not smooth, resulting in a high temperature of the condenser itself, which in turn affects the overall cooling effect of the refrigeration component.

[0044] On the oil smoke flow path, the condenser 24 is arranged downstream of the fan 12, and can be directly connected to the air outlet of the fan 12, or connected to the fan 12 through an air outlet cover (not shown, which is the prior art), and a smoke exhaust pipe (not shown) is connected downstream of the condenser 24. That is, the space surrounded by the inner layer of the heat conducting plate 2411 of the first part 2413 of the main body 241 (to be described in detail below) constitutes a smoke exhaust channel 2412 through which the oil smoke exhausted by the fan 12 passes before reaching the public flue or being discharged into the room.

[0045] In this embodiment, the condenser 24 is directly arranged at the air outlet of the fan 12 and arranged vertically. Affected by the height of the range hood module, the kitchen ceiling and the cabinet, the height of the condenser 24 is generally as low as possible. The height of the condenser 24 is h, and preferably h≤400mm, and preferably h=350mm in this embodiment. The main body 241 includes a first part 2413, which is a hollow rectangular parallelepiped with openings at both ends (the condenser 24 is arranged vertically, that is, the upper and lower ends are open). Since the heat dissipation area of ​​the first part 2413 alone is not enough, a curling process is performed inside the first part 2413. That is, the main body 241 also includes a second part 2414, which is an integral structure with the first part 2413. Here, the integral means that the first part 2413 and the second part 2414 can be an integrally formed structure, or the first part 2413 and the second part 2414 can be made into an integral structure by welding, etc., or the first part 2413 and the second part 2414 can be a structure formed by direct or indirect contact. The second part 2414 is located inside the space enclosed by the first part 2413, and the second part 2414 and the first part 2413 form a heat conduction path through direct contact. The second part 2414 extends inward from the wall surface of the first part 2413 (here "inward" only means curling inside the space enclosed by the first part 2413, and does not indicate the starting point and curling direction of curling during manufacturing), and the height direction is consistent with the first part 2413. In this embodiment, the definition of the height direction being consistent means that the height directions of the two coincide, or a small angle tilt caused by the manufacturing process is allowed, such as an angle of -5° to 5° in the height direction. In this embodiment, the height directions of the first part 2413 and the second part 2414 coincide, that is, both are vertical directions. The second part 2414 is curled, and there are many forms of curling. Preferably, in this embodiment, the second part 2414 is a spiral cylinder, and can also be curled into an elliptical roll, a circular roll or other forms of rolls.

[0046] The second part 2414 has n+1 winding layers, where n is a natural number ≥ 2, and the distance between the innermost layer located at or near the center and the adjacent layer is d 11 , the distance between the second layer near the center and the adjacent layer outside is d 12 , and so on, the distance between the outermost layer and its adjacent layer is d 1n When n = 2, the distance between the second layer near the center and its outer adjacent layer, that is, the distance between the outermost layer and its adjacent layer, d 12 That is d 1n. The spacing between two adjacent layers here refers to taking a point on a relatively inner layer (the point is located on the side of the layer facing the outer layer) on any end face of the second part 2414 along the height direction (the upper end face or the lower end face in the installed state, and the refrigerant channel 242 and the edge 2417 do not exist on the end face), and obtaining the minimum spacing between it and the relatively outer layer, and successively taking other points on the relatively inner layer to obtain a minimum spacing value respectively, and taking the average of all the minimum spacing values ​​as the spacing between two adjacent layers. When making comparisons below, the spacing values ​​between each two adjacent layers are compared with the results calculated on the same end face. Figure 6 In the embodiment shown, n=4. The above spacing satisfies the following relationship: d 11 ≤d 12 ...≤d 1n , when n = 2, d 12 That is d 1n The following effects can be achieved: 1) The central wind speed is high, which can make the central high wind speed area diffuse outward, improve the rectification effect of oil smoke, and make the oil smoke pass through the condenser 24 to be discharged at a uniform speed; 2) Since the distance in the center is small, the resistance is large, which can increase the probability of oil smoke colliding with the second part 2414, thereby improving the filtering effect, and the high wind speed area diffuses outward on the outside, which increases the wind volume on the outside, so that more oil smoke contacts the second part 2414, thereby improving the filtering effect on the outside; 3) Since the high wind speed area diffuses outward on the outside of the second part 2414, the speed of taking away the heat of the condenser 24 can be increased, thereby improving the heat exchange efficiency.

[0047] In addition, the above-mentioned spacing values ​​are all within the range of 5 mm to 200 mm (the above-mentioned range includes the two end points) to facilitate the passage of oil smoke.

[0048] Optionally, n can also be 1, see Fig.11 As shown, the second part 2414 is only curled to form an inner and outer layer. In the direction of the second part 2414 rotating from the center to the outside, on any end face of the second part 2414 in the height direction (the upper end face or the lower end face in the installed state, on which there is no refrigerant channel 242 and edge 2417), the minimum distance between any point on the side of the inner layer facing the outer layer and the outer layer is d 11x , the minimum distance between any point after this point and the outer layer is d 11y , and satisfies d 11x ≤d 12y The effect is the same as when n≥2.

[0049] From the end face of the main body 241, as shown Figure 6 The top view shown, or Fig.11In the bottom view shown, the cross-sectional area of ​​the smoke exhaust channel 2412 surrounded by the first part 2414 is S1, and the cross-sectional area of ​​the second part 2414 (the sum of the areas on the same cross section) is S2, and S2≤0.005S1 is satisfied. As a result, the cross-sectional area of ​​the second part 2414 is much smaller than the cross-sectional area of ​​the smoke exhaust channel 2412, avoiding the second part 2414 from causing greater resistance to the exhaust of oil smoke due to occupying a larger proportion of the smoke exhaust channel 2412, ensuring that the oil smoke can still be discharged smoothly. The cross-sectional area here refers to the area on the horizontal cross section when the embodiment is placed vertically.

[0050] The first inner wall surface 2415 of the inner heat conducting plate 2411 of the first part 2413 facing the exhaust passage 2412 and the first outer wall surface 2416 of the outer heat conducting plate 2411 away from the inner heat conducting plate 2411 both constitute heat dissipation surfaces. The inner heat dissipation surface dissipates heat through the oil smoke passing through the exhaust passage 2412, and the outer heat dissipation surface contacts the room temperature air entering the second shell 21 from the kitchen indoor environment during operation, and can also achieve a certain degree of heat dissipation. In the second part 2414, the second inner wall surface 2418 of the inner heat conducting plate 2411 facing the center and the second outer wall surface 2419 of the outer heat conducting plate 2411 facing the first part 2413 are both in contact with the oil smoke, and both constitute heat dissipation surfaces, with a large heat dissipation area and a good heat dissipation effect.

[0051] The area of ​​the first inner wall surface 2415 of the first portion 2413 is S 11 , the area of ​​the first outer wall of the first part 2413 is S 12 , the area of ​​the second inner wall surface 2418 of the second portion 2414 is S 21 , the area of ​​the second outer wall of the second portion 2414 is S 22 , and satisfy S 21 +S 22 ≥0.6(S 11 +S 12 ), so that the second part 2414 has sufficient heat dissipation area to fully increase the center wind speed to improve the heat dissipation efficiency.

[0052] The volume of the refrigerant channel 242 on the first part 2413 is V1, the volume of the refrigerant channel 242 on the second part 2414 is V2, and V2≥V1 is satisfied, so that when the refrigerant flows into the refrigerant channel of the second part, a larger amount of refrigerant can utilize the high central wind speed to improve the heat dissipation efficiency.

[0053] In addition, the main body 241 can be conveniently arranged through the first part 2413 of the outer rectangular parallelepiped shape, and in particular, the main body 241 can be directly arranged at the air outlet of the fan 12 (all of which can match the rectangular cross section). The condenser 24 as a whole is also at least partially inwardly rolled, and has a larger area in contact with the oil smoke under the same volume, which can further improve the overall heat exchange efficiency. In addition, since the wind speed in the center of the condenser 24 is fast, it is convenient to dissipate heat faster.

[0054] On the basis of the two heat conducting plates 2411 formed by hot rolling, a part is first rolled into a spiral shape to obtain the second part 2414, and then the remaining plate is rolled into a cuboid, and the joint seams are welded.

[0055] The bottom of the first part 2413 of the main body 241 is formed with a flange 243 bent outward, which is used to be fixed to the top of the first shell 11 and directly connected to the air outlet of the fan 12. The flange 243 can be fixed to the first shell 11 by screws. As a result, the heat of the main body 241 can be conducted to the first shell 11 with a larger heat dissipation area and the metal connecting parts such as the volute of the fan 12 by heat conduction, which is equivalent to a wider heat transfer area under the action of airflow and a better heat dissipation effect. In order to ensure that the heat of the main body 241 is better conducted to the first shell 11, the flange 243 of the condenser 24 and the first shell 11 can be coated with thermal conductive glue, thereby improving heat transfer and better sealing of the connection after assembly and extrusion to prevent oil smoke leakage.

[0056] The upper end of the first part 2413 of the main body 241 can be connected to a circular smoke exhaust duct (not shown) through a square-to-circular adapter 3. The adapter 3 is similar to an inverted air outlet hood commonly used in the art, and the main body 241 and the adapter 3 can be fixed by screws.

[0057] See also Figure 7, the refrigerant channel 242 has at least two. The condenser 24 also includes an inlet manifold 246, an outlet manifold 247, a first collector 244 and a second collector 245, wherein the inlet manifold 246 is connected to the compressor 22 through a pipeline, and can receive the refrigerant from the compressor 21, the inlet manifold 246 is divided to one end of each refrigerant channel 242 through the first collector 244, and the other end of each refrigerant channel 242 is connected to the outlet manifold 247 after being collected through the second collector 244, and the outlet manifold 247 is connected to the evaporator 23 through a pipeline, and can transport the refrigerant after heat exchange to the evaporator 23. The formation of each collector and the manifold is the same as that of the refrigerant channel 242. By setting the first collector 244, the refrigerant flowing in from the inlet manifold 246 can be evenly divided into each refrigerant channel 242, and by setting the second collector 245, it is convenient for the refrigerant in each refrigerant channel 242 to be collected and then flow out. The sum of the cross-sectional areas of the refrigerant channels 242 is greater than the cross-sectional area of ​​the inlet manifold 246 and the outlet manifold 247, so as to meet the target inlet-outlet pressure difference and allow the pipe path to be appropriately lengthened without causing a significant pressure drop at the outlet, thereby increasing the heat exchange capacity.

[0058] The cross-section of the refrigerant channel 242 (edge ​​2417) may be circular. The circular design can reduce the risk of the refrigerant channel 242 being flattened at the bend when the main body 241 is curled. As for the oil smoke resistance, the cross-section shape satisfies the following conditions: Figure 5 and Fig.10 , the refrigerant channel 242 has a vertical channel 2421 extending vertically and a transverse channel 2422 extending transversely (similarly, the edge 2417 of the main body 241 has a vertical extension portion corresponding to the vertical channel 2421 and a transverse extension portion corresponding to the transverse channel 2422), and the bends of the vertical channel 2421 and the transverse channel 2422 are close to 90 degrees. The edge 2417 of the transverse extension portion corresponding to the transverse channel 2422 on the inner side of the first part 2413 of the main body 241, and the edge 2417 of the transverse extension portion corresponding to the transverse channel 2422 of the second part 2414 of the main body 241, on the cross section of the refrigerant channel 242 ( Figure 5 The outer contour of the edge 2417, on the side facing the oil smoke (only the inner side of the first part 2413 faces the oil smoke, and both sides of the second part 2414 facing the center and away from the center face the oil smoke), has the lowest point A, the vertical line passing through the lowest point A is the Y axis, the point on the outer contour that is the largest distance from the Y axis in the horizontal direction is B, the horizontal line passing through point B is the X axis, and the intersection of the X axis and the Y axis is the coordinate origin O, thereby constructing a coordinate system, the distance between point A and the origin O is a, the distance between point B and the origin O is b, the length of the line between point A and point B is d, and the following conditions are satisfied: a>b, The line AB is a continuous curve, a broken line, a combination of a curve and a straight line, or a combination of a curve and a broken line that bulges away from the origin O. Here, the curve can be a smooth curve or multiple curves connected end to end. The combination of a curve and a straight line can be a curve connected to one or more straight lines, and the combination of a curve and a broken line is the same. In this embodiment, a smooth curve is preferred. The angle formed by the straight line between point A and point B and the Y axis is α, and α is less than 45°.

[0059] In this embodiment, preferably, the portion of the main body 241 that forms the refrigerant channel 242 is a structure of equal wall thickness. According to the flow of the refrigerant in the condenser 24 and the heat transfer analysis on the air side of the fume extraction module, it is determined that in the scenario where the condenser 24 uses the high wind speed of the fume extraction module to dissipate heat, the cross-sectional shape of the refrigerant channel 242 (the cross-sectional shape of the edge 2417) can be an ellipse. Therefore, the following description will be given by taking the inner circumference of the cross section of the refrigerant channel 242 as an example. It should be noted that since the heat conducting plate 2411 has a certain thickness, the ellipse of the cross section of the edge 2417 is not a closed figure in the strict sense, but forms a spacing at both ends of the major axis that is the same as the plate thickness. The major axis length of the edge 2417 is 2a' (greater than 2a), and the minor axis length is 2b' (greater than 2b). The major axis length of the ellipse of the inner circumference of the cross section of the refrigerant channel 242 is 2a", and the minor axis length is 2b". The cross-sectional area s = πa”b”, the circumference of the ellipse p = 2πb”+4(a”-b”), then the equivalent diameter of the elliptical cross section is D h =4s / p.

[0060] For analysis of equivalent diameter and cross-sectional area pressure, see Table 1:

[0061] <![CDATA[Cross-sectional area (mm 2 )]]> Equivalent diameter(mm) Pressure drop(Pa) 5.97 2.42 83217 15.76 4.24 8090 19.06 4.66 5268

[0062] Table 1 Pressure analysis of equivalent diameter and cross-sectional area

[0063] The above experimental data takes four refrigerant channels 242 as an example. It can be seen that the cross-sectional area has a significant effect on the refrigerant pressure drop and changes exponentially. The smaller the cross-sectional area, the higher the refrigerant flow resistance in the condenser 24, the greater the refrigeration system power, and thus affects the exhaust temperature of the compressor 21 and causes the system to be unreliable. In this embodiment, the cross-sectional area of ​​the refrigerant channel 242 is preferably 3mm 2 ~25mm 2 .

[0064] Analysis of the velocity flow field on the air side shows that since the main body 241 of the condenser 24 has a raised edge 2417 at the position corresponding to the refrigerant channel 242 and the main body 241 has a constant wall thickness, the cross section of the refrigerant channel 242 has the same peripheral shape as the cross section of the main body 241 and the refrigerant channel 242 at the corresponding position. Fig. 9As can be seen from the left part (from left to right, the oil smoke passes through the plane, the elliptical protrusion and the circular protrusion), under the same oil smoke flow rate (v = 70m / s), as the cross section of the corresponding position of the main body 241 and the refrigerant channel 242 approaches from a circle to an ellipse, the generated vortex is smaller, and the resistance to the oil smoke flow at the corresponding position of the main body 241 and the refrigerant channel 242 is reduced. Therefore, in this embodiment, the cross section of the refrigerant channel 242 is preferably an ellipse. As can be seen from the analysis examples 1 to 5 on the right part, when the cross-sectional area of ​​the refrigerant channel 242 is maintained at the same level, the oil smoke flow resistance of case-3 (analysis example 3, Dh = 4.02mm) is increased by about 30% compared with case-5 (analysis example 5, Dh = 3.04mm), that is, the larger the equivalent diameter, the greater the resistance to the oil smoke. Therefore, when the cross-sectional area is the same, the smaller the equivalent diameter, the better. For this reason, in this embodiment, it is preferred to satisfy 1 < a " / b" ≤ 5 (that is, 1 < a' / b' ≤ 5). However, the larger the ratio, the better. If it is too large, the refrigerant channel will be flattened at the bend when the main body is curled, thereby increasing the fluid resistance.

[0065] The more bends the refrigerant channel 242 has, the higher the resistance is, and the heat transfer efficiency is correspondingly improved. The bends refer to the bends of the refrigerant channel 242. See Table 2:

[0066] serial number Equivalent two-pass pressure difference Heat transfer Two-pipe 8090Pa 1520W Two-bend single pipe 13872Pa 1754W Multiple bends single pass 17906Pa 1933W

[0067] Table 2: Tube length, pressure difference and heat transfer test table

[0068] In the above Table 2, two pipe passes means that the inlet manifold 246 and the outlet manifold 247 are on the same side. Figure 7 The figures are all on the left side, and will be on the same side after winding. Single pipe pass means that the inlet manifold 246 and the outlet manifold 247 are on both sides. Figure 7 In the same deployed state, one of the inlet manifold 246 and the outlet manifold 247 is on the left side and the other is on the right side.

[0069] The cross section of the transverse channel 2422 is an ellipse, and the long axis direction of the ellipse is consistent with the oil smoke flow path. Figure 5The vertical direction is shown in the figure. The ratio of the total length of the vertical channel 2421 to the total length of the transverse channel 2422 is not less than 1.1. The vertically extending ridge 2417 corresponding to the vertical channel 2421 is conducive to the downward flow of the oil accumulated on the wall of the main body 241 relative to the transverse channel 2422, and is also conducive to guiding the oil smoke upward to reduce turbulence. At the same time, when the oil smoke rises, it contacts half of the ridge 2417 corresponding to the vertical channel 2421 (that is, it completely contacts the surface of the ridge 2417 on the inner side of the main body 241), and can only contact the lower 1 / 4 of the ridge 2417 corresponding to the transverse channel 2422 (that is, it can only contact the lower half of the surface of the ridge 2417 on the inner side of the main body 241). Therefore, even with the same length, the vertical channel 2421 can better achieve heat exchange, and if the length of the vertical channel 2421 is larger, the heat exchange area is larger, and the heat exchange effect is better.

[0070] A prototype of the applicant was tested, and the test value of the grease separation degree of the prototype was 92.7%. However, referring to Table 3 below, after adding the condenser 24, the test value of the grease separation degree was 95.1%, and the grease separation degree was greatly improved:

[0071]

[0072]

[0073] Table 3: Grease separation test table

[0074] Embodiment 2

[0075] See also Figure 12 to Figure 14 In this embodiment, the difference from the above-mentioned embodiment 1 is that the second part 2414 is arranged at intervals inside the space surrounded by the first part 2413. Preferably, it can be a hollow cylinder with openings at both ends of the axial direction, and is arranged at the center of the first part 2413. The second part 2414 is not provided with a refrigerant channel 242, but only serves as a heat conductor. A heat conductive sheet 248 is connected between the inner side wall of the first part 2413 and the outer side wall of the second part 2414. The heat conductive sheet 248 can have at least two and is distributed radially. The second part 2414 and the heat conductive sheet 248 are both made of heat conductive materials and can conduct heat, such as made of metal, more preferably made of aluminum. As a result, an indirect contact heat conduction path is formed between the second part 2414 and the first part 2413 through the heat conductive sheet 248.

[0076] When manufacturing the condenser 24, firstly, the second part 2414 and the heat conductive sheet 248 are evenly arranged along the circumference and fully welded, and then grooves are made at corresponding angles in the axial direction of the main body 241, so that the second part 2414 and the heat conductive sheet 248 are aligned and placed, and then the connection between the main body 241 and the heat conductive sheet 248 is welded, so that the heat of the main body 241 can be well transferred to the internal heat conductive sheet 248 part and the second part 2414. The second part 2414 and the heat conductive sheet 248 can well rectify the uneven flow of the airflow in the original smoke exhaust channel 2412 into a uniform flow, better contact the inner wall surface of the main body 241, the second part 2414 and the heat conductive sheet 248, and the heat dissipation effect is greatly optimized.

[0077] The "fluid communication" referred to in the present invention refers to the spatial position relationship between two parts or parts (hereinafter collectively referred to as the first part and the second part), that is, the fluid (gas, liquid or a mixture of the two) can flow from the first part along the flow path or / and be transported to the second part. The first part and the second part can be directly connected, or the first part and the second part can be indirectly connected through at least one third party. The third party can be a fluid channel such as a pipe, channel, duct, guide member, hole, groove, etc., or it can be a chamber allowing fluid to flow through, or a combination of the above.

Claims

1. A condenser of a refrigeration range hood, comprising a refrigerant channel (242); characterized in that: The condenser also includes a main body (241) capable of conducting heat, and the refrigerant channel (242) is arranged on the main body (241). The main body (241) includes a first part (2413) and a second part (2414). The first part (2413) is in the shape of a pipe and encloses a smoke exhaust channel (2412) for oil smoke to pass through. The second part (2414) is arranged in a space enclosed by the first part (2413) and forms a heat conduction path with the first part (2413) through direct contact or indirect contact. From the end face of the main body (241), the cross-sectional area of ​​the smoke exhaust channel (2412) enclosed by the first part (2413) is S1, and the cross-sectional area of ​​the second part (2414) is S2, S2≤0.005S1.

2. The condenser of the refrigeration range hood according to claim 1, characterized in that: The first part (2413) includes a first inner wall surface (2415) in contact with the oil smoke and a first outer wall surface (2416) not in contact with the oil smoke, and the second part (2414) includes a second inner wall surface (2418) and a second outer wall surface (2419) both in contact with the oil smoke. The first inner wall surface (2415) and the first outer wall surface (2416) of the first part (2413) and the second inner wall surface (2418) and the second outer wall surface (2419) of the second part (2414) all constitute heat dissipation surfaces.

3. The condenser of the refrigeration range hood according to claim 2, characterized in that: The area of ​​the first inner wall surface (2415) of the first portion (2413) is S 11 , the area of ​​the first outer wall (2416) of the first part (2413) is S 12 , the area of ​​the second inner wall surface (2418) of the second portion (2414) is S 21 , the area of ​​the second outer wall surface (2419) of the second portion (2414) is S 22 , and satisfy S 21 +S 22 ≥0.6(S 11 +S 12 ).

4. The condenser of the refrigeration range hood according to any one of claims 1 to 3, characterized in that: The main body (241) has a gap formed inside the wall of only the first portion (2413), and the gap directly constitutes the refrigerant channel (242).

5. The condenser of the refrigeration range hood according to any one of claims 1 to 3, characterized in that: A refrigerant channel (242) is provided on both the first part (2413) and the second part (2414); the volume of the refrigerant channel (242) on the first part (2413) is V1, the volume of the refrigerant channel (242) on the second part (2414) is V2, and V2≥V1 is satisfied.

6. The condenser of the refrigeration range hood according to any one of claims 1 to 3, characterized in that: Part of the refrigerant channel (242) is directly formed by the gap inside the wall of the main body (241), and a raised ridge (2417) is formed at the corresponding position of the main body (241) and the refrigerant channel (242). The refrigerant channel (242) has at least a transverse channel (2422) extending laterally. On the cross section of the refrigerant channel (242), the outer contour of the ridge (2417) corresponding to the transverse channel (2422) has a lowest point A on the side facing the oil smoke, and the vertical line passing through the lowest point A is the Y-axis. The point on the outer contour that is the largest distance from the Y-axis in the horizontal direction is B, and the horizontal line passing through point B is the X-axis. The intersection of the X-axis and the Y-axis is the origin (O), the distance between point A and the origin (O) is a, the distance between point B and the origin (O) is b, and the angle formed by the straight line connecting point A and point B and the Y-axis is α, and α is less than 45°.

7. The condenser of the refrigeration range hood according to any one of claims 1 to 3, characterized in that: The second portion (2414) is formed by extending the wall surface of the first portion (2413) inwardly.

8. The condenser of the refrigeration range hood according to claim 7, characterized in that: The second part (2414) has n+1 winding layers, n is a natural number ≥ 3, and the distance between the innermost layer located at or near the center and the adjacent layer is d 11 , the distance between the second layer near the center and the adjacent layer outside is d 12 , and so on, the distance between the outermost layer and its adjacent layer is d 1n , each spacing value is within the range of 5 mm to 200 mm; or, the second part (2414) has n+1 winding layers, n=2, and the spacing between the innermost layer located at or near the center and the adjacent layer is d 11 , the distance between the second layer near the center and the adjacent layer outside is d 12 , each spacing value is in the range of 5mm to 200mm.

9. A refrigeration range hood, comprising a range hood assembly and a refrigeration assembly, wherein the range hood assembly comprises a first shell (11) and a fan (12) arranged in the first shell (11); characterized in that: The refrigeration assembly comprises a condenser according to any one of claims 1 to 8, wherein the condenser is connected to the first shell (11) and is arranged at the air outlet of the fan (12).

10. The refrigeration range hood according to claim 9, characterized in that: The first part (2413) of the main body (241) is a vertically arranged rectangular parallelepiped, and a flange (243) bent outward is formed at the bottom of the first part (2413) of the main body (241), and the flange (243) is fixed to the top of the first shell (11).

11. The refrigeration range hood according to claim 10, characterized in that: The refrigerant channel (242) of the condenser includes a vertical channel (2421) and a transverse channel (2422). The transverse channel (2422) is bent relative to the vertical channel (2421). The main body (241) of the condenser is raised at a position corresponding to the refrigerant channel (242) to form a ridge (2417). On a cross section perpendicular to the extension direction of the refrigerant channel (242), the outer contour of the ridge (2417) is consistent with the contour shape of the refrigerant channel (242). The ratio of the total length of the vertical channel (2421) to the total length of the transverse channel (2422) is not less than 1.1.

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