Condenser of refrigeration extractor hood and refrigeration extractor hood

Abstract

The utility model discloses a condenser of a refrigeration range hood and the refrigeration range hood, the condenser comprises a refrigerant channel and a main body capable of conducting heat, and the main body is in a pipeline shape; a gap is formed in the wall part of the main body, the gap forms at least two fluid passages, and at least one fluid passage is at least one part of a refrigerant passage through which a refrigerant passes so as to be in direct contact with the main body. Compared with the prior art, the condenser has the advantages that a plurality of passages are formed in the main body of the condenser, so that refrigerants and cooling liquid can be introduced at the same time, and the refrigerants can also be introduced in all the passages, and the heat exchange efficiency is improved.

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 the need for additional power. However, since the condenser is wrapped around the exhaust pipe, it is usually not possible to ensure that the condenser can be completely close to the exhaust pipe when it is 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 pipe wall of the condenser, and the long heat exchange path will lead to low heat exchange efficiency. In addition, the condenser only dissipates heat through the oil smoke, and most of the oil smoke does not contact the condenser when passing through the condenser, and cannot drive the heat of the condenser, resulting in low heat exchange efficiency. The poor heat dissipation effect of the condenser will directly affect the cooling effect of the range hood air conditioner, so it needs further improvement. 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.

[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 above-mentioned first technical problem is: a condenser of a refrigeration range hood, including a refrigerant channel, characterized in that:

[0009] The condenser comprises a main body capable of conducting heat, and the main body is in the shape of a pipe;

[0010] A gap is formed inside the wall of the main body, and the gap constitutes at least two fluid passages, at least one of which is at least a part of the refrigerant channel through which the refrigerant passes and is in direct contact with the main body.

[0011] By making the condenser as a whole in the shape of a pipe, the inside of the condenser can dissipate heat through the oil smoke passing through the inside of the pipe, and the outside can dissipate heat through the air in the external environment, and the heat transfer path between the refrigerant channel and the heat-dissipating oil smoke or air is short, so that the refrigerant flowing inside the condenser tube wall can be fully dissipated, thereby improving the overall heat exchange efficiency, and then the refrigeration effect of the refrigeration component; and multiple passages are formed, through which the refrigerant and cooling liquid can pass at the same time, or all of them can pass the refrigerant, to improve the heat exchange efficiency.

[0012] According to one aspect of the utility model, at least one of the fluid passages is a cooling channel for cooling liquid for dissipating heat from the condenser to pass through and thus directly contact the main body, and the cooling channel is independent of the refrigerant channel.

[0013] Preferably, the cooling liquid may be condensed water produced by an evaporator.

[0014] According to another aspect of the utility model, each fluid passage is a refrigerant channel, and the refrigerant channel has a refrigerant inlet and a refrigerant outlet, and each refrigerant channel shares the refrigerant inlet and the refrigerant outlet.

[0015] According to one aspect of the utility model, the refrigerant channel is spiral-shaped.

[0016] Preferably, the height of the condenser is L 1 The cross-sectional perimeter of the refrigerant channel is L 2 The cross-sectional perimeter of the refrigerant channel per unit height of the condenser is L 2 / L 1 , and satisfy L 2 / L 1 The range is 0.002~0.012, thereby making the refrigerant and the heat-conducting body have more contact area, increasing the heat dissipation area and improving the heat dissipation effect.

[0017] Furthermore, each fluid passage is a refrigerant channel, the refrigerant channel has a refrigerant inlet and a refrigerant outlet, and each refrigerant channel shares the refrigerant inlet and the refrigerant outlet;

[0018] The main body is arranged vertically, and a first liquid collecting chamber and a second liquid collecting chamber are formed inside the wall of the main body. Each liquid collecting chamber extends vertically, and the first liquid collecting chamber is connected to the refrigerant inlet and the refrigerant outlet respectively to be fluidically connected. When passing through each liquid collecting chamber, the refrigerant channel penetrates the liquid collecting chamber at the corresponding position. The design of the double liquid collecting chamber reduces the length of the refrigerant channel, so the flow resistance of the refrigerant in the pipeline is smaller, the pressure drop on the refrigerant side is small, and the lower pressure drop on the refrigerant side brings better heat exchange effect.

[0019] According to another aspect of the utility model, the refrigerant channel includes at least three vertically extending first channels, a second channel connected between the upper ends of two adjacent first channels, and a third channel connected between the lower ends of two adjacent first channels, and the second channel and the third channel extend in opposite directions at both ends of the same first channel.

[0020] The width of the horizontal cross section of the condenser is L 3 The cross-sectional perimeter of the refrigerant channel is L 4 The cross-sectional perimeter of the refrigerant channel per unit width of the condenser is L 4 / L 3 , L 4 / L 3 The range is 0.04 to 0.3, which allows the refrigerant and the heat-conducting body to have more contact area, increases the heat dissipation area, and improves the heat dissipation effect.

[0021] Preferably, at least one refrigerant channel has a circular cross section, and the diameter of the refrigerant channel is ≤1 mm. The refrigerant channel is a microchannel, which effectively reduces the flow area of ​​the refrigerant, has a smaller inner diameter, a higher refrigerant flow rate, and a better heat exchange effect of the condenser. It also allows the refrigerant to have more contact area with the heat-conducting body, and the heat dissipation effect is also better.

[0022] Preferably, in order to ensure a shorter refrigerant heat transfer path, the main body includes two layers of heat conducting plates, and the fluid passage is formed between the two layers of heat conducting plates.

[0023] Furthermore, the condenser further comprises a columnar curled body curled in the space enclosed by the main body, a gap is formed inside the wall of the columnar curled body, and the gap constitutes a part of the refrigerant channel for the refrigerant to pass through and directly contact the columnar curled body, the fluid passages on the main body are all refrigerant channels, and the volume of the refrigerant channel on the columnar curled body is V 1 The volume of the refrigerant channel on the main body is V 2 , and satisfy V 1 / (V1 +V 2 )≥40%. The setting of the columnar curled body allows the high wind speed in the center to expand outward, thereby improving the heat exchange efficiency. By setting a refrigerant channel inside the wall of the columnar curled body, the heat exchange area can be increased in a limited space, and the formation of the refrigerant channel makes the heat exchange path shorter, further improving the heat exchange efficiency; in addition, by meeting a certain volume ratio of the refrigerant channel, as much heat as possible is placed in the center to be taken away by the oil smoke, reducing the influence of the main heat radiation of the condenser on the compressor / evaporator, especially the influence of heat radiation on the compressor.

[0024] Furthermore, the two layers of heat conducting plates have a gap only at a position where the fluid passage is formed.

[0025] The technical solution adopted by the utility model to solve the second technical problem is: a refrigeration range hood, including a fume suction component and a refrigeration component, characterized in that: the refrigeration component includes the condenser as described above, the condenser is arranged on the fume exhaust path of the refrigeration range hood, and along the fume flow path, the condenser is arranged downstream of the fume suction component. The condenser is arranged on the fume exhaust path, that is, the condenser can be communicated / connected with the fume exhaust port / fume exhaust pipe, or the condenser is a part of the fume exhaust pipe.

[0026] Preferably, the refrigeration assembly is arranged above the oil fume suction assembly, thereby making it easy to install the refrigeration assembly and also reducing the space occupied on both sides of the oil fume suction assembly.

[0027] Preferably, the oil fume suction assembly comprises a first shell and a fan arranged in the first shell;

[0028] The refrigeration assembly further includes a second shell, a compressor and an evaporator. The compressor, the evaporator and the condenser are arranged in the second shell. The second shell is arranged on the first shell.

[0029] Compared with the prior art, the advantages of the utility model are: by making the condenser as a whole in the shape of a pipe, the interior can dissipate heat through the oil smoke passing through the inside of the pipe, and the outside can dissipate heat through the air in the external environment, and the heat transfer path between the refrigerant channel and the heat-dissipating oil smoke or air is short, so that the refrigerant flowing inside the condenser tube wall can be fully dissipated, thereby improving the overall heat exchange efficiency, and thus improving the refrigeration effect of the refrigeration component; and multiple passages are formed, which can pass refrigerant and cooling liquid at the same time, or all of them can pass refrigerant, so as to improve the heat exchange efficiency; when all of the refrigerant passes or multiple refrigerant channels are formed, the contact area between the refrigerant and the heat-conducting component is larger, and the heat exchange effect is better. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] Figure 1 A schematic diagram of a range hood according to a first embodiment of the utility model;

[0031] Figure 2 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;

[0032] Figure 3 It is a partial schematic diagram of a refrigeration assembly of a range hood according to a first embodiment of the utility model;

[0033] Figure 4 It is a schematic diagram of a condenser of a refrigeration assembly of a range hood according to a first embodiment of the utility model;

[0034] Figure 5 It is a cross-sectional view of a condenser of a refrigeration assembly of a range hood according to a first embodiment of the utility model;

[0035] Figure 6 for Figure 5 A schematic diagram of the partial enlargement of Ⅰ;

[0036] 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;

[0037] Figure 8 A schematic diagram of a range hood according to a second embodiment of the utility model, in which a range hood exhaust assembly and a refrigeration assembly respectively hide part of the housing;

[0038] Fig. 9 A schematic diagram of a condenser of a refrigeration assembly of a range hood according to a second embodiment of the utility model;

[0039] Fig.10 A cross-sectional view of a condenser of a refrigeration assembly of a range hood according to a second embodiment of the utility model;

[0040] Fig.11 for Fig.10 A partial II enlarged schematic diagram of

[0041] Fig.12 A schematic diagram of a condenser of a refrigeration assembly of a range hood according to a third embodiment of the utility model;

[0042] Fig.13 It is a schematic diagram of the expansion of the condenser of the refrigeration assembly of the range hood according to the third embodiment of the utility model;

[0043] Fig.14 A schematic diagram of a condenser of a refrigeration assembly of a range hood according to a fourth embodiment of the utility model;

[0044] Fig.15 A cross-sectional view of a condenser of a refrigeration assembly of a range hood according to a fourth embodiment of the utility model;

[0045] Fig.16 It is a schematic diagram of a condenser of a refrigeration assembly of a range hood according to a fifth embodiment of the utility model. DETAILED DESCRIPTION

[0046] 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.

[0047] 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.

[0048] Embodiment 1

[0049] 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. Optionally, it can be any form of existing top suction, low suction, ceiling type, etc. The first shell 11 can be a combination of one or more shells.

[0050] 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.

[0051] 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.

[0052] A cold air outlet 211 is provided on the front side of the second housing 21, such as near the top. The evaporator 23 can be arranged near the cold air outlet 211. The cold air after heat exchange in the evaporator 23 is blown out from the cold air outlet 211 into the kitchen through the cooling fan 25 to provide a comfortable cooking environment temperature for the user. Air inlets 212 are provided on other sides of the second housing 21, such as the left and right sides, to replenish air (room temperature air) into the second housing 21.

[0053] The condenser 24 includes a main body 241 and a fluid passage. The main body 241 is in the shape of a hollow pipe, preferably a cylindrical shape, and the fluid passage is formed inside the wall of the main body 241. In this embodiment, the main body 241 is arranged vertically, especially vertically, and the opposite ends of the main body 241 (the upper and lower ends in this embodiment) are open. The wall of the main body 241 includes two layers of heat conducting plates 2411, and the fluid passage 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 fluid passage is formed, and are fitted in other parts (the gap existing in the non-fluid passage due to process problems is regarded as a situation without gap). Optionally, the heat conducting plate 2411 is a metal plate, such as an aluminum plate, which is preferably hot-rolled and pressed, and the space between the two aluminum plates is inflated to form the above-mentioned fluid passage, and then the whole is rolled into a desired shape. After hot rolling, the refrigerant in the fluid passage can withstand a pressure of up to 2.3MPa, and there is zero gap contact between the refrigerant and the heat-conducting material, and the heat exchange efficiency is extremely high, so the surface temperature of the condenser under natural conditions is not higher than 50°C. However, 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.

[0054] The fluid passages have at least two, at least one of which is a refrigerant channel 242 for refrigerant to pass through. The refrigerant channel 242 has a refrigerant inlet 2421 and a refrigerant outlet 2422 .

[0055] On the oil fume flow path, the condenser 24 is arranged downstream of the fan 12, and it can be directly connected to the air outlet of the fan 12, or connected to the fan 12 through the air outlet cover 13, or connected to the smoke exhaust pipe (not shown) as a part of the smoke exhaust pipe. That is, the space surrounded by the heat conducting plate 2411 of the inner layer of the main body 241 constitutes a smoke exhaust channel 2412 through which the oil fume exhausted by the fan 12 passes before reaching the public flue or being discharged into the room, and the inner wall surface of the inner layer of the heat conducting plate 2411 (i.e. the inner wall surface of the main body 241) and the outer wall surface of the outer layer of the heat conducting plate 2411 (i.e. the outer wall surface of the main body 241) both constitute heat dissipation surfaces. The inner heat dissipation surface dissipates heat through the oil fume passing through the smoke exhaust channel 2412, and the outer heat dissipation surface contacts the room temperature air entering the second housing 21 from the kitchen indoor environment during operation, and can also achieve a certain degree of heat dissipation. The room temperature air constitutes a heat dissipation fluid.

[0056] The height of the condenser 242 is L 1 The cross-sectional perimeter of the refrigerant channel 242 is L 2 The cross-sectional perimeter of the refrigerant channel 242 per unit height of the condenser is L 2 / L 1 , and satisfy L 2 / L 1 The range is 0.002 to 0.012. The cross section shown in the figure is a polygon or a circle. The number of refrigerant channels 242 can be 1 or at least 2. The greater the number, the longer the total circumference of the refrigerant channels 242, or the longer the circumference of a single refrigerant channel 242, the greater the contact area with the main body 241, and the better the heat dissipation effect. In order to further improve the heat exchange efficiency, at least one of the fluid passages is a cooling channel 243 for cooling liquid to pass through, which is independent of the refrigerant channel 242. See Figure 7 , in order to clearly illustrate the relationship between the refrigerant channel 242 and the cooling channel 243, the condenser 24 is shown in the unfolded state, and the cooling channel 243 has a cold water inlet 2431 and a cold water outlet 2432. Liquid for cooling, such as condensed water, can be introduced into the cooling channel 243, and external tap water can also be connected. The flow direction of the refrigerant in the refrigerant channel 242 and the cooling liquid in the cooling channel 243 can be consistent. For example, in the present embodiment, both channels are arranged in a spiral shape, and both inlets are located at the upper end. The arrows indicate the flow direction of the refrigerant and the cooling liquid. Alternatively, the cold water inlet 2431 can also be at the lower end.

[0057] Embodiment 2

[0058] See also Figure 8 to Figure 11In this embodiment, the difference from the above-mentioned embodiment 1 is that a first liquid collecting chamber 2441 and a second liquid collecting chamber 2442 are further formed inside the wall of the main body 241, and each liquid collecting chamber extends vertically and is arranged relative to each other in the circumferential direction, preferably symmetrically. The first liquid collecting chamber 2441 is respectively connected to the refrigerant inlet 2421 and the refrigerant outlet 2422 for fluid communication, and a transversely arranged partition 2443 is provided in the first liquid collecting chamber 2441 to separate the first liquid collecting chamber 2441 into two parts, the upper and lower parts, and the partition 2443 is used to isolate refrigerants with different flow directions.

[0059] In this embodiment, the fluid passage includes three independent refrigerant channels 242, and each refrigerant channel 242 passes through the corresponding liquid collecting chamber when passing through the liquid collecting chamber, so that each liquid collecting chamber separates each refrigerant channel 242, forming a channel with smaller lengths and each section connected through the liquid collecting chamber. Fig.10 As shown by the arrows in , the flow path of the refrigerant is that after the refrigerant enters from the refrigerant inlet 2421, part of the refrigerant flows downward from the three refrigerant channels 242 respectively until it enters the second liquid collecting chamber 2442 downward, and part of the refrigerant entering the second liquid collecting chamber 2442 goes directly downward, while part of it can reversely enter the space below the partition 2443 in the first liquid collecting chamber 2441 from the refrigerant channel 242 located below the partition 2443, and finally flow out from the refrigerant outlet 2422; while part of the refrigerant goes directly downward from the first liquid collecting chamber 2441, and can enter the refrigerant channel 242 at the corresponding position of the partition 2443 in the first liquid collecting chamber 2441, and after passing through the second liquid collecting chamber 2442, it again passes through the refrigerant channel 242 located below the partition 2443 and reversely enters the space below the partition 2443 in the first liquid collecting chamber 2441, and finally flows out from the refrigerant outlet 2422.

[0060] At least one refrigerant channel 242 is a microchannel with a circular cross section, and the diameter of a single refrigerant channel 242 is preferably ≤1 mm, thereby effectively reducing the flow area of ​​the refrigerant, the inner diameter of the refrigerant channel 242 is smaller, the refrigerant flow rate is greater, and the heat exchange effect of the condenser 24 is better. This microchannel design can also be applied to the first embodiment and the following third embodiment.

[0061] The design of the microchannel also ensures the relative area of ​​the heat dissipation fins connected to the refrigerant channel 242 to a greater extent, and the heat dissipation area is large, so the heat exchange effect is better. The design of the double liquid collecting chamber also reduces the length of the refrigerant channel 242, so the flow resistance of the refrigerant in the pipeline is smaller, the pressure drop on the refrigerant side is small, and the lower the pressure drop on the refrigerant side, the better the heat exchange effect.

[0062] Embodiment 3

[0063] See also Fig.12 and Fig.13In this embodiment, the difference from the above-mentioned embodiment 1 is that the refrigerant channel 242 is in a vertical parallel reflux shape, and the refrigerant channel 242 includes at least three vertically extending first channels 2423, a second channel 2424 connected between the upper ends of two adjacent first channels 2423, and a third channel 2425 connected between the lower ends of two adjacent first channels 2423. The second channel 2424 and the third channel 2425 are arranged in a staggered manner, that is, the second channel 2424 and the third channel 2425 extend in opposite directions at both ends of the same first channel 2423, the second channel 2424 extends in the direction of one of the adjacent first channels 2423 of the first channel 2423, and the third channel 2425 extends in the direction of the other adjacent first channel 2423 of the first channel 2423. The second channel 2424 is in an upwardly convex curved shape, preferably an arc shape, and the third channel 2425 is in a downwardly convex curved shape, preferably also an arc shape. There are also three refrigerant channels 242, and each refrigerant channel 242 shares a refrigerant inlet 2421 and a refrigerant outlet 2422. Fig.12 One of the refrigerant channels 242 is shown in FIG. Fig.13 Three refrigerant channels 242 are shown in FIG. 1 , and arrows indicate the flow paths of the refrigerant.

[0064] The width of the horizontal cross section of the condenser 24 is L 3 , the cross-sectional perimeter of the refrigerant channel 242 is L 4 The cross-sectional perimeter of the refrigerant channel per unit width of the condenser is L 4 / L 3 , L 4 / L 3 The range is 0.04 to 0.3. In the present embodiment, the condenser 24 is cylindrical, so the width is its diameter. Alternatively, the condenser 24 may be a rectangular parallelepiped, in which case the width refers to the larger of the width and length of the rectangle. The number of refrigerant channels 242 may be 1 or at least 2. The greater the number, the longer the total circumference of the refrigerant channels 242, or the longer the circumference of a single refrigerant channel 242, which means that the greater the area in contact with the main body 241, the better the heat dissipation effect.

[0065] Embodiment 4

[0066] See also Fig.14 and Fig.15In this embodiment, the difference from the above-mentioned embodiment 1 is that the condenser 24 also includes a columnar curled body 245 curled in the space enclosed by the main body 241. Therefore, the arrangement of the columnar curled body 243 allows the central high wind speed to expand outward, thereby improving the heat exchange efficiency. A gap is formed inside the wall of the columnar curled body 245, and the gap constitutes a coolant channel 242 (a part of the coolant channel 242 of the condenser 24) for the coolant to pass through and directly contact the columnar curled body 245. The fluid passages on the main body 241 are all coolant channels 242, and the volume of the coolant channel 242 on the columnar curled body 245 is V 1 , the volume of the refrigerant channel 242 on the main body 241 is V 2 , and satisfy V 1 / (V 1 +V 2 )≥40%. By arranging the refrigerant channel 242 inside the wall of the columnar curled body 243, the heat exchange area can be increased in a limited space, and the formation of the refrigerant channel 242 makes the heat exchange path shorter, and the heat exchange efficiency is further improved. In addition, by meeting a certain volume ratio of the refrigerant channel 242, as much heat as possible is placed in the center to be taken away by the oil smoke, reducing the influence of the heat radiation of the main body 241 of the condenser 24 on the compressor 22 / evaporator 23, especially the influence of the heat radiation on the compressor 23.

[0067] Embodiment 5

[0068] See also Fig.16 In this embodiment, the difference from the above-mentioned fourth embodiment is that the main body 241 is a hollow rectangular parallelepiped, while the main body 241 in the fourth embodiment is a hollow cylinder.

[0069] 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 comprises a main body (241) capable of conducting heat, and the main body (241) is in the shape of a pipe; A gap is formed inside the wall of the main body (241), and the gap constitutes at least two fluid passages, at least one of which is at least a part of the refrigerant channel (242) through which the refrigerant passes and is in direct contact with the main body (241).

2. The condenser of the refrigeration range hood according to claim 1, characterized in that: At least one of the fluid passages is a cooling channel (243) through which cooling liquid for dissipating heat from the condenser passes, thereby directly contacting the main body (241), and the cooling channel (243) and the refrigerant channel (242) are independent of each other.

3. The condenser of the refrigeration range hood according to claim 1, characterized in that: Each fluid passage is a refrigerant channel (242), and the refrigerant channel (242) has a refrigerant inlet (2421) and a refrigerant outlet (2422). Each refrigerant channel (242) shares the refrigerant inlet (2421) and the refrigerant outlet (2422).

4. The condenser of the refrigeration range hood according to claim 1, characterized in that: The refrigerant channel (242) is spiral-shaped.

5. The condenser of the refrigeration range hood according to claim 4, characterized in that: The height of the condenser is L1, the cross-sectional perimeter of the refrigerant channel (242) is L2, the cross-sectional perimeter of the refrigerant channel (242) per unit height of the condenser is L2 / L1, and the range of L2 / L1 is 0.002 to 0.

012.

6. The condenser of the refrigeration range hood according to claim 4, characterized in that: Each fluid passage is a refrigerant channel (242), and the refrigerant channel (242) has a refrigerant inlet (2421) and a refrigerant outlet (2422), and each refrigerant channel (242) shares the refrigerant inlet (2421) and the refrigerant outlet (2422); The main body (241) is arranged vertically, and a first liquid collecting chamber (2441) and a second liquid collecting chamber (2442) are formed inside the wall of the main body (241). Each liquid collecting chamber extends vertically. The first liquid collecting chamber (2441) is respectively connected to the refrigerant inlet (2421) and the refrigerant outlet (2422) for fluid communication. The refrigerant channel (242) penetrates the liquid collecting chambers at corresponding positions when passing through each liquid collecting chamber.

7. The condenser of the refrigeration range hood according to claim 1, characterized in that: The refrigerant channel (242) includes at least three vertically extending first channels (2423), a second channel (2424) connected between the upper ends of two adjacent first channels (2423), and a third channel (2425) connected between the lower ends of two adjacent first channels (2423), and the second channel (2424) and the third channel (2425) extend in opposite directions at both ends of the same first channel (2423).

8. The condenser of the refrigeration range hood according to claim 7, characterized in that: The width of the horizontal cross section of the condenser is L3, the cross-sectional perimeter of the refrigerant channel (242) is L4, and the cross-sectional perimeter of the refrigerant channel per unit width of the condenser is L4 / L3, and the range of L4 / L3 is 0.04 to 0.

3.

9. The condenser of the refrigeration range hood according to claim 1, characterized in that: The cross section of at least one refrigerant channel (242) is circular, and the diameter of the refrigerant channel (242) is ≤1 mm.

10. The condenser of the refrigeration range hood according to claim 1, characterized in that: The condenser also includes a columnar curled body (245) curled in a space enclosed by the main body (241), and a gap is formed inside the wall of the columnar curled body (245). The gap constitutes a part of the refrigerant channel (242) for the refrigerant to pass through and thus directly contact the columnar curled body (245). The fluid passages on the main body (241) are all refrigerant channels (242), the volume of the refrigerant channel (242) on the columnar curled body (245) is V1, and the volume of the refrigerant channel (242) on the main body (241) is V2, and V1 / (V1+V2)≥40% is satisfied.

11. The condenser of the refrigeration range hood according to any one of claims 1 to 10, characterized in that: The wall portion of the main body (241) includes two layers of heat conducting plates (2411), and the fluid passage is formed between the two layers of heat conducting plates (2411).

12. A refrigeration range hood, comprising a range hood assembly and a refrigeration assembly, characterized in that: The refrigeration component comprises a condenser according to any one of claims 1 to 11, wherein the condenser is arranged on the smoke exhaust path of the refrigeration range hood, and along the smoke flow path, the condenser is arranged downstream of the smoke exhaust component.

13. The refrigeration range hood according to claim 12, characterized in that: The refrigeration component is arranged on the oil fume suction component.

14. The refrigeration range hood according to claim 13, characterized in that: The oil fume suction assembly comprises a first shell (11) and a fan (12) arranged in the first shell (11); The refrigeration assembly further comprises a second shell (21), a compressor (22) and an evaporator (23); the compressor (22), the evaporator (23) and the condenser are arranged in the second shell (21); and the second shell (21) is arranged on the first shell (11).

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