Evaporator, refrigeration assembly and ice food processor

Abstract

The utility model discloses an evaporator, refrigeration assembly and ice food processor, and the evaporator includes bottom plate, and the bottom plate recess forms the accommodation groove and the installation part around the accommodation groove, and the installation part is used for connecting in refrigeration disc, to make the refrigeration disc close the slot of the accommodation groove, the bottom plate sets up the entrance and the export of intercommunication the accommodation groove, the bottom plate recess forms the separation from the groove bottom of the accommodation groove to the slot of the accommodation groove, to form the flow channel, and the entrance and the export respectively intercommunication two ends of the flow channel, through this evaporator, the evaporator is connected to the refrigeration disc, and after the refrigerant is passed into the flow channel, the heat transfer path between the evaporator and the refrigeration disc is: refrigerant refrigeration disc, shortens the heat transfer path, reduces the heat loss in the heat transfer process, and improves the refrigeration efficiency to the refrigeration disc.

Description

Technical Field

[0001] This utility model relates to the field of refrigeration technology, and in particular to an evaporator, a refrigeration component, and an ice food processor. Background Technology

[0002] In scenarios requiring both refrigeration and efficient heat exchange, such as in ice cream makers and other similar equipment, evaporators are often necessary to facilitate heat exchange. For example, an ice cream maker, also known as a shaved ice machine, is characterized by a cooling plate as the main operating space. The working surface of the cooling plate is typically below 0°C. Users pour liquids such as water or milk onto the cooling plate and stir it. After a certain period of cooling, the desired shaved ice, ice cream, or other food products are formed.

[0003] Ice food processors typically require an evaporator connected to a refrigeration system to cool the food. During normal operation, a low-temperature, low-pressure gas-liquid mixture of refrigerant flows through the evaporator.

[0004] In existing technologies, evaporators typically have pipes installed, and the heat transfer path for cooling the refrigeration plate is: refrigerant → pipe → refrigeration plate, which is a long heat transfer path. In addition, the actual heat transfer area is the contact area between the pipe and the refrigeration plate, where heat conduction is limited, the utilization rate of refrigerant is not high, the heat transfer efficiency is low, and the heat transfer efficiency is greatly affected by the pipe diameter.

[0005] After optimizing the heat transfer path from refrigerant to pipe to cooling plate, a heat-conducting component (such as an aluminum plate) is installed between the pipe and the cooling plate by connecting them with a hot melt adhesive layer and a backing adhesive layer. The heat transfer path is: refrigerant → pipe → hot melt adhesive layer → heat-conducting component → backing adhesive layer → cooling plate. This method enhances the heat transfer uniformity, but still has the drawbacks of a long heat transfer path and low cooling efficiency. Utility Model Content

[0006] In view of the above problems, the present invention provides an evaporator, a refrigeration component, and an ice food processor, which overcomes or at least partially solves the above problems.

[0007] According to one aspect of the present invention, an evaporator is provided, including a base plate, the base plate being recessed to form a receiving groove and a mounting portion surrounding the receiving groove, the mounting portion being used to connect to a refrigeration plate so that the refrigeration plate closes the opening of the receiving groove; the base plate being provided with an inlet and an outlet communicating with the receiving groove; the base plate being recessed from the bottom of the receiving groove toward the opening of the receiving groove to form a partition portion to form a flow channel, the inlet and the outlet respectively communicating with the two ends of the flow channel.

[0008] In one alternative embodiment, the side of the mounting portion facing away from the bottom of the receiving groove is flush with the side of the partition portion facing away from the receiving groove, and the side of the partition portion facing away from the receiving groove is used to connect to the cooling plate.

[0009] In one alternative embodiment, the partition includes a first segment extending along a first direction, wherein the starting end of the first segment is connected to the mounting portion along the first direction, and a gap exists between the terminating end of the first segment and the mounting portion; along a second direction perpendicular to the first direction, the first segment and the mounting portion form a first portion of the flow channel, the inlet being located in the first portion and disposed near the region where the starting end of the first segment is connected to the mounting portion; along the second direction, the first segment is recessed toward the first portion to form a protrusion; along the second direction, a first region is formed between the protrusion and the mounting portion, the first region being disposed near the inlet.

[0010] In one alternative approach, in the region corresponding to the flow channel, the bottom plate is recessed from the bottom of the receiving groove toward the opening of the receiving groove to form a raised structure and a diversion area. The number of diversion areas is two, and the two diversion areas are arranged opposite to each other on both sides of the raised structure along the second direction.

[0011] In one alternative embodiment, the side of the protrusion facing away from the receiving groove is flush with the side of the mounting portion facing away from the bottom of the receiving groove, and the side of the protrusion facing away from the receiving groove is used to connect to the cooling plate.

[0012] In one alternative, the flow channel is formed with a narrow neck region.

[0013] In one alternative embodiment, the number of protruding structures is multiple, the number of narrow neck regions is multiple, and the protruding structures and narrow neck regions are alternately arranged along the direction of the flow channel.

[0014] In one alternative embodiment, along the first direction, the distance from the first region to the inlet is L, and the diameter of the inlet is d, where L > 5d; and / or, the width of the first region along the second direction is greater than the diameter of the inlet; and / or, along the second direction, the width of the neck region is greater than the width of the diversion region; and / or, the cross-sectional area of ​​the neck region is S1, and the cross-sectional area of ​​the diversion region is S2, where S1:S2 = 2:1.

[0015] According to one aspect of the present invention, a refrigeration assembly is provided, including the evaporator; the mounting portion is connected to the refrigeration plate, and the refrigeration plate closes the opening of the receiving groove.

[0016] According to one aspect of the present invention, an ice food processor is provided, including a housing, a refrigeration system, an electronic control system, and the refrigeration components disposed in the housing; the electronic control system is connected to the refrigeration system, the inlet and the outlet are respectively connected to the refrigeration system, and the refrigeration system is used to supply refrigerant to the flow channel.

[0017] The beneficial effects of this utility model embodiment include: providing an evaporator, the evaporator including a base plate, the base plate being provided with a partition to form a flow channel. Through this evaporator, the evaporator is connected to a refrigeration plate. After refrigerant is introduced into the flow channel, the heat transfer path between the evaporator and the refrigeration plate is: refrigerant → refrigeration plate, which shortens the heat transfer path, reduces heat loss during the heat transfer process, and improves the refrigeration efficiency of the refrigeration plate.

[0018] In addition, compared with the existing technology that uses pipes for heat transfer, where the actual heat transfer area is the contact area between the pipe and the cooling plate, the refrigerant in the flow channel of this utility model acts directly on the cooling plate, which is not limited by the area of ​​the contact area between the pipe and the cooling plate, nor by the diameter of the pipe. This results in high refrigerant utilization and high heat transfer efficiency. Attached Figure Description

[0019] One or more embodiments are illustrated by way of example with reference numerals in the accompanying drawings. These illustrations do not constitute a limitation on the embodiments. Elements with the same reference numerals in the drawings are denoted as similar elements. Unless otherwise stated, the figures in the drawings are not to be limited by scale.

[0020] Figure 1 This is a schematic diagram of an evaporator and refrigeration plate with pipes in the prior art.

[0021] Figure 2 This is a schematic diagram of an evaporator and refrigeration plate with pipes and heat-conducting components in the prior art.

[0022] Figure 3 This is a schematic diagram of the evaporator provided in an embodiment of the present invention.

[0023] Figure 4 This is a schematic diagram of the refrigeration component provided in an embodiment of the present invention.

[0024] Figure 5 This is an exploded view of the refrigeration component provided in an embodiment of this utility model.

[0025] Figure 6 This is a partial schematic diagram of the front view of the evaporator provided in an embodiment of this utility model.

[0026] Figure 7 This is a schematic diagram of the flow path of the evaporator provided in an embodiment of this utility model.

[0027] Figure 8 The embodiment of this utility model provides the following... Figure 6 A sectional view of P.

[0028] Figure 9 This is a schematic diagram of the evaporator provided in another embodiment of the present invention.

[0029] Figure 10 This is a schematic diagram of the ice food processor provided in this embodiment of the utility model.

[0030] The labels in the attached diagram are as follows: 10p, Evaporator in the prior art; 101p, Pipe of evaporator in the prior art; 20p, Cooling plate in the prior art; 30p, Hot melt adhesive layer in the prior art; 40p, Heat-conducting component in the prior art; 50p, Backing adhesive layer in the prior art; 10. Evaporator; R, flow channel; R1, First section; R11, First region; R12, Diversion region; R13, Neck region; R2, Part Two; R3, Part Three; C1, direction of flow channel; D1, first direction; D2, second direction; 1. Base plate; g. Gap; 1s, receiving slot; 1g, slot opening; 1a, inlet; 1b, outlet; 1c, corner position; 11. Mounting section; 12. Partition section; 13. Protruding structure; 111. The side of the mounting section facing away from the bottom of the receiving groove; 1201. The side of the partition section facing away from the receiving groove; 121. First section; 122. Second section; 123. Third section; 1211. Protrusion; 131. The side of the protruding structure facing away from the receiving groove; 100. Refrigeration component; 2. Refrigeration plate; 21. Working surface; 22. Mounting surface; 3. Inlet pipe; 4. Outlet pipe; 1000. Ice food processor; 5. Shell. Detailed Implementation

[0031] To facilitate understanding of this utility model, a more detailed description is provided below with reference to the accompanying drawings and specific embodiments. It should be noted that when an element is described as "fixed to" another element, it can be directly on the other element, or one or more intermediate elements may exist between them. When an element is described as "connected to" another element, it can be directly connected to the other element, or one or more intermediate elements may exist between them. The terms "vertical," "horizontal," "left," "right," "inner," "outer," and similar expressions used in this specification are for illustrative purposes only.

[0032] Unless otherwise defined, all technical and scientific terms used in this specification have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the scope of the invention. The term "and / or" as used in this specification includes any and all combinations of one or more of the associated listed items.

[0033] To facilitate readers' understanding of the design concept of this utility model, the evaporator 10p and the refrigeration plate 20p in the prior art are briefly described below.

[0034] Please see Figure 1 In the prior art, the evaporator 10p is equipped with a pipe 101p, which is bent, coiled, and fixed to the refrigeration plate 20p. For example, the pipe 101p is fixed to the refrigeration plate 20p by welding. The pipe 101p is used for the inflow and outflow of refrigerant. The material of the pipe 101p can be copper or other metals with good thermal conductivity to ensure efficient heat exchange performance. Figure 1 In the existing technology, the heat transfer path is: refrigerant → pipe 101p → cooling plate 20p, which is a long heat transfer path. In addition, the actual heat transfer area is the contact area between pipe 101p and cooling plate 20p, where heat conduction is limited, the utilization rate of refrigerant is not high, the heat transfer efficiency is low, and the heat transfer efficiency is greatly affected by the diameter of pipe 101p.

[0035] Please see Figure 2 , Figure 2 This illustrates another structure of an evaporator 10p and a cooling plate 20p in the prior art. Figure 2 In this design, the evaporator 10p is equipped with a pipe 101p, which is bent and coiled for the inflow and outflow of refrigerant. The pipe 101p can be made of aluminum or other metals with good thermal conductivity to ensure efficient heat exchange. The pipe 101p is bonded to the heat-conducting component 40p via a hot-melt adhesive layer 30p. The heat-conducting component 40p can be an aluminum plate or other materials with good thermal conductivity. The heat-conducting component 40p is then fixedly connected to the cooling plate 20p via a backing adhesive layer 50p. Figure 2 In the existing technology, the heat transfer path is: refrigerant → pipe 101p → hot melt adhesive layer 30p → heat-conducting component 40p → backing adhesive layer 50p → cooling plate 20p. This method enhances the uniformity of heat transfer by setting the heat-conducting component 40p, but it still has the defects of long heat transfer path and low cooling efficiency.

[0036] Please see Figure 3 The evaporator 10 provided in this embodiment of the present invention includes a base plate 1, wherein the base plate 1 is recessed to form a receiving groove 1s and a mounting portion 11 surrounding the receiving groove 1s. Please refer to... Figure 4 and Figure 5 The mounting part 11 is used to connect to the refrigeration plate 2 so that the refrigeration plate 2 closes the slot opening 1g of the receiving groove 1s; the base plate 1 is provided with an inlet 1a and an outlet 1b connecting the receiving groove 1s; the base plate 1 is recessed from the bottom of the receiving groove 1s toward the slot opening 1g to form a partition part 12, so as to form a flow channel R, and the inlet 1a and the outlet 1b are respectively connected to the two ends of the flow channel R. In practical applications, the mounting part 11 of the base plate 1 of the evaporator 10 is connected to the refrigeration plate 2. The refrigerant flows in from the inlet 1a, flows through the flow channel R, and flows out from the outlet 1b. During the flow process, the refrigerant directly contacts the refrigeration plate 2 for heat exchange. The heat transfer path between the evaporator 10 and the refrigeration plate 2 is: refrigerant → refrigeration plate 2. The refrigerant and the refrigeration plate 2 directly exchange heat, the heat transfer path is short, the heat loss during the heat transfer process is small, and the evaporator 10 has high refrigeration efficiency for the refrigeration plate 2.

[0037] Furthermore, unlike existing technologies that use pipe 101p for heat transfer, and where the actual heat transfer area is between pipe 101p and cooling plate 20p (e.g., ... Figure 1 As shown in the figure, the refrigerant in the flow channel R acts directly on the cooling plate 2 in this embodiment of the invention, with different contact positions. This method is not limited by the contact area between the pipe 101p and the cooling plate 2, nor by the diameter of the pipe 101p, thus resulting in higher refrigerant utilization and higher heat transfer efficiency.

[0038] In some embodiments, please refer to Figure 3 and combination Figure 4 , Figure 5The side 111 of the mounting part 11 facing away from the bottom of the receiving groove 1s is flush with the side 1201 of the partition part 12 facing away from the receiving groove 1s. The side 1201 of the partition part 12 facing away from the receiving groove 1s is used to connect to the refrigeration plate 2. The side 111 of the mounting part 11 facing away from the bottom of the receiving groove 1s is also used to connect to the refrigeration plate 2. When the mounting part 11 is connected to the refrigeration plate 2, and the partition part 12 is connected to the refrigeration plate 2, a stable and reliable connection interface can be formed between the refrigeration plate 2 and the mounting part 11 or the partition part 12 of the base plate 1. On the one hand, this avoids the connection gap between the mounting part 11 and the refrigeration plate 2, ensuring the sealed flow of the refrigerant in the flow channel R and reducing the risk of refrigerant leakage. On the other hand, it avoids the connection gap between the partition part 12 and the refrigeration plate 2, facilitating the formation of a single flow direction of the refrigerant in the flow channel R, preventing the refrigerant from splitting or flowing turbulently in the flow channel R, and ensuring heat exchange efficiency.

[0039] It is worth noting that the function of the partition 12 is to form a flow channel R for refrigerant flow within the receiving tank in 1 second. The layout design of the partition 12 allows for adjustment of the direction C1 and length of the flow channel R, thereby optimizing the refrigerant flow path, extending the refrigerant residence time within the flow channel R, and improving the adequacy of heat exchange. The layout of the partition 12 can be varied. For example, the partition 12 can be bent and coiled to form a U-shaped structure (not shown in the figure), in which case the bending and coiling direction of the partition 12 corresponds to the direction C1 of the flow channel R; or the partition 12 can be bent and coiled to form an S-shape (or serpentine shape). Alternatively, the partition 12 can be formed into other structural forms to optimize the refrigerant flow path. For example, in some embodiments, the partition 12 includes a first segment 121, a second segment 122, and a third segment 123. The first segment 121 extends along a first direction D1, with its starting end connected to the mounting portion 11. A gap g exists between the terminating end of the first segment 121 and the mounting portion 11, forming part of a flow channel R. The second segment 122 extends along the first direction D1, with its terminating end connected to the mounting portion 11. A gap g exists between the starting end of the second segment 122 and the mounting portion 11, forming part of a flow channel R. The third segment 123 extends along the first direction D1, with its starting end connected to the mounting portion 11. A gap g exists between the terminating end of the third segment 123 and the mounting portion 11, forming part of a flow channel R. Through the design of the multi-segment partition 12 described above, an S-shaped flow channel R is formed (such as...). Figure 3As shown in the diagram, the overall direction of the flow channel R, C1, is S-shaped, allowing the refrigerant to flow along a longer path within a limited space, thus improving the cooling effect on the cooling coil 2. It can be understood that the direction of the flow channel R, C1, defines the flow direction of the refrigerant within the channel R.

[0040] The third section 123, the second section 122, and the first section 121 are arranged at intervals along the second direction D2, wherein the second direction D2 is perpendicular to the first direction D1 and parallel to the base plate 1 (mounting part 11). Along a second direction D2 perpendicular to the first direction D1, the first segment 121 and the mounting portion 11 form a first portion R1 of the flow channel R, with the inlet 1a located in the first portion R1 and positioned near the area where the starting end of the first segment 121 connects to the mounting portion 11. Correspondingly, a second portion R2 of the flow channel R is formed between the second segment 122 and the first segment 121, and the second portion R2 connects to the first portion R1 through a gap g between the terminating end of the first segment 121 and the mounting portion 11. A third portion R3 of the flow channel R is formed between the third segment 123 and the second segment 122, and the third portion R3 connects to the second portion R2 through a gap g between the starting end of the second segment 122 and the mounting portion 11. The gap g between the terminating end of the third segment 123 and the mounting portion 11 connects to the outlet 1b. This design allows the refrigerant to flow from inlet 1a through the first part R1 of the flow channel R, then through the second part R2 and the third part R3, and finally out from outlet 1b. The refrigerant completes a meandering flow within the S-shaped flow channel R, ensuring the heat exchange effect.

[0041] In some embodiments, there are multiple second segments 122 and multiple third segments 123. Multiple third segments 123 and multiple second segments 122 are alternately arranged along the second direction D2. The number of second segments 122 and the number of third segments 123 can be reasonably set according to actual needs, thereby adjusting the complexity of the flow channel R and the length of the flow channel R along its direction C1.

[0042] When there are multiple second sections 122 and multiple third sections 123, the second section 122 closest to the first section 121 along the second direction D2 forms the second part R2 of the flow channel R between the second section 122 and the first section 121; the third section 123 closest to the first section 121 along the second direction D2 forms the third part R3 of the flow channel R between the second section 122 closest to the first section 121; the remaining adjacent third sections 123 and second sections 122 sequentially form subsequent parts of the flow channel R, until the third section 123 (or second section 122) furthest from the first section 121 along the second direction D2 connects to the outlet 1b between the space between it and the mounting part 11, thereby extending the flow path of the refrigerant and improving the heat exchange effect.

[0043] In some embodiments, the first segment 121 may meander along a first direction D1, wherein the first direction D1 is a straight direction and is the direction in which the first segment 121 extends as a whole. In practical applications, the first direction D1 can be used as a design reference. For example, the first direction D1 is parallel to one of the outer edges of the mounting portion 11, and the first segment 121 may meander along this first direction D1.

[0044] In some implementations, the first direction D1 is approximately the direction of the line connecting the beginning of the first segment 121 to the end of the first segment 121.

[0045] It is understandable that the first segment 121 can extend regularly along the first direction D1, for example, in a wavy shape.

[0046] Similarly, the second section 122 and the third section 123 can both extend meanderingly along the first direction D1.

[0047] Similarly, the second segment 122 and the third segment 123 can both extend regularly along the first direction D1, for example, in a wave-like shape.

[0048] It is understood that in some embodiments, the second section 122 and the third section 123 may not be provided, and the partition 12 and the mounting section 11 may cooperate to form a flow channel R for refrigerant flow.

[0049] Please continue reading for more details. Figure 3The specific locations of the inlet 1a and the outlet 1b can be reasonably set according to actual needs. For example, the receiving groove 1s of the base plate 1 has several (e.g., 4) corner positions 1c. The inlet 1a penetrates the bottom of the receiving groove 1s, and the outlet 1b penetrates the bottom of the receiving groove 1s. The inlet 1a is located at one of the corner positions 1c, and the outlet 1b is located at one of the corner positions 1c. The corner position 1c where the inlet 1a is located and the corner position 1c where the outlet 1b is located are distributed in two adjacent corner positions 1c on one side of the receiving groove 1s (e.g., Figure 3 (as shown), or, the corner position 1c where the inlet 1a is located and the corner position 1c where the outlet 1b is located are distributed at both ends of the diagonal of the receiving groove 1s to adapt to different installation layout requirements.

[0050] In some embodiments, please refer to Figure 6 Along the second direction D2, the first section 121 is recessed towards the first portion R1 of the flow channel R to form a protrusion 1211; along the second direction D2, a first region R11 is formed between the protrusion 1211 and the mounting portion 11, and the first region R11 is located near the inlet 1a. The first region R11 is a part of the flow channel R, and the first region R11 is used to guide the refrigerant to enter from the inlet 1a, mix, and then diffuse.

[0051] It is worth noting that in some embodiments, please refer to [the relevant documentation]. Figure 6 In the region corresponding to the flow channel R, the bottom plate 1 is recessed from the bottom of the receiving groove 1s toward the opening 1g of the receiving groove 1s to form a raised structure 13 and a diversion region R12. There are two diversion regions R12, which are arranged opposite each other on both sides of the raised structure 13 along the second direction D2. The diversion region R12 is part of the flow channel R. Through the arrangement of the raised structure 13 and the diversion region R12, the refrigerant in the flow channel R is turbulent and diverted. Figure 7 (Indicated by arrows), disrupting the smooth and regular laminar boundary layer, enhancing turbulence, causing refrigerant flow disorder, and promoting the interaction between the refrigerant and the cooling coil 2 (e.g., Figure 4 The heat mixing and transfer between the refrigerant and the cooling plate 2 (as shown) increases the heat exchange rate between the refrigerant and the cooling plate 2, improves the heat transfer coefficient, and enhances the cooling effect on the cooling plate 2.

[0052] The number of the protruding structures 13 can be multiple, with one protruding structure 13 corresponding to two flow-dividing regions R12. Multiple protruding structures 13 are arranged sequentially and at intervals along the direction C1 of the flow channel R to form a multi-level turbulence and flow-dividing structure, thereby gradually breaking up the laminar flow pattern of the refrigerant, further enhancing the turbulence effect, and improving the overall heat exchange uniformity of the refrigerant.

[0053] It is worth noting that in some embodiments, please refer to [the relevant documentation]. Figure 6 and combination Figure 5 The side 131 of the protruding structure 13 facing away from the receiving groove 1s is flush with the side 111 of the mounting part 11 facing away from the bottom of the receiving groove 1s. The side 131 of the protruding structure 13 facing away from the receiving groove 1s is also flush with the side 1201 of the partition part 12 facing away from the receiving groove 1s. The side 131 of the protruding structure 13 facing away from the receiving groove 1s is used to connect to the refrigeration plate 2. When the mounting part 11 is connected to the refrigeration plate 2, and when the partition part 12 is connected to the refrigeration plate 2, the protruding structure 13 is also connected to the refrigeration plate 2. The base plate 1 is connected to the refrigeration plate 2 through the mounting part 11, the partition part 12, and the protruding structure 13, ensuring the reliability of the connection between the base plate 1 and the refrigeration plate 2. Furthermore, by connecting the protruding structure 13 to the refrigeration plate 2, there is almost no gap between the protruding structure 13 and the refrigeration plate 2, which not only effectively avoids local stagnation of refrigerant caused by gaps, but also ensures the turbulent effect of the protruding structure 13 on the refrigerant.

[0054] It is worth noting that in some embodiments, please refer to [the relevant documentation]. Figure 6 The flow channel R has a narrow neck region R13. The narrow neck region R13 is a narrow section of the flow channel R. The narrow neck region R13 increases the flow velocity of the refrigerant, reduces local pressure, further breaks the laminar flow state, and enhances turbulence intensity. In some embodiments, there are multiple protruding structures 13 and multiple narrow neck regions R13. Along the direction C1 of the flow channel R, the protruding structures 13 and the narrow neck regions R13 are alternately arranged to form a multi-stage turbulence and acceleration structure, progressively increasing the turbulence of the refrigerant, further improving the heat transfer coefficient, and enhancing the performance of the cooling plate 2 (e.g., Figure 5 The cooling effect is shown in the figure.

[0055] In some embodiments, please continue reading Figure 6 Along the second direction D2, partially protruding structures 13 and narrow neck regions R13 are alternately arranged. A portion of the flow channel R forms a protruding structure 13 and a flow-dividing region R12, while another portion of the flow channel R forms a narrow neck region R13, improving processing convenience. For example, a protruding structure 13 and a flow-dividing region R12 are formed between the third segment 123 closest to the first segment 121 along the second direction D2 and the second segment 122 closest to the first segment 121 along the second direction D2; a narrow neck region R13 is formed between the second segment 122 closest to the first segment 121 along the second direction D2 and the first segment 121; and a protruding structure 13 and a flow-dividing region R12 are formed between the first segment 121 and the mounting portion 11. Alternatively, please refer to [further details omitted]. Figure 6A narrow neck region R13 is formed between the third segment 123, which is closest to the first segment 121 along the second direction D2, and the second segment 122, which is closest to the first segment 121 along the second direction D2. A protruding structure 13 and a diversion region R12 are formed between the second segment 122, which is closest to the first segment 121 along the second direction D2, and the first segment 121. A narrow neck region R13 is formed between the first segment 121 and the mounting portion 11. Alternatively, please refer to [further details omitted]. Figure 6 A narrow neck region R13 is formed between the third segment 123, which is closest to the first segment 121 along the second direction D2, and the second segment 122, which is closest to the first segment 121 along the second direction D2. A protruding structure 13 and a diversion region R12 are formed between the second segment 122, which is closest to the first segment 121 along the second direction D2, and the first segment 121. The aforementioned protruding portion 1211 and a first region R11 for mixing the refrigerant are formed between the first segment 121 and the mounting portion 11.

[0056] In one implementation, please refer to [link / reference]. Figure 6 and combination Figure 7 One of the plurality of protruding structures 13 (the same as the first protruding structure 13 below) is positioned close to the first region R11, and one of the plurality of narrow neck regions R13 (the same as the first narrow neck region R13 below) is positioned close to the first region R11. Along the first direction D1, the inlet 1a, the first region R11, and one of the plurality of protruding structures 13 and one of the plurality of narrow neck regions R13 are sequentially arranged, so that after the refrigerant enters the flow channel R from the inlet 1a, it first passes through the first region R11 for mixing and diffusion, and then impacts the adjacent first protruding structure 13, initiating initial turbulence. With the help of the two side flow splitting regions R12, the mainstream flow is divided and guided, enhancing the local turbulence intensity. Subsequently, the refrigerant flows through the first narrow neck region R13, where the flow velocity increases sharply and the pressure decreases, further breaking the laminar boundary and significantly enhancing the turbulence effect. Then, it sequentially passes through multiple alternating protruding structures 13 and narrow neck regions R13, achieving step-by-step turbulence and acceleration, keeping the refrigerant in a high-intensity turbulent state and effectively improving heat exchange efficiency.

[0057] It is worth noting that in some embodiments, such as Figure 6 As shown, along the first direction D1, the distance from the first region R11 to the inlet 1a is L, and the diameter of the inlet 1a is d, where L > 5d. For example, the diameter of the inlet 1a is 6.3 mm, and the distance from the first region R11 to the inlet 1a is 32 mm. This limitation ensures that the first region R11 mixes the refrigerant sufficiently and effectively, reducing the risk of uneven mixing due to the short distance.

[0058] In some embodiments, please refer to Figure 6 and combination Figure 8The width W1 of the first region R11 along the second direction D2 is greater than the diameter d of the inlet 1a. The cross-section of the first region R11 is approximately semi-circular, and the cross-section of the first region R11 is the shape obtained by cutting the first region R11 with a plane perpendicular to the first direction D1. Since the width W1 of the first region R11 along the second direction D2 is greater than the diameter d of the inlet 1a, the area of ​​the cross-section of the first region R11 (π(W1 / 2)) 2 / 2) The area that can approach the entrance 1a (π(d / 2)) 2 This ensures the flow space of the refrigerant after it enters the flow channel R from the inlet 1a, reducing the risk of flow blockage.

[0059] For example, the diameter d of the inlet 1a is 6.3 mm, the width W1 of the first region R11 along the second direction D2 is 9 mm, and the area of ​​the cross section of the first region R11 is (π(W1 / 2)). 2 / 2) = (π(9 / 2)) 2 / 2) = 31.8mm 2 The area of ​​entrance 1a is π (6.3 / 2). 2 ) = (π (d / 2) 2 =31.2mm 2 .

[0060] In some embodiments, such as Figure 6 As shown, along the second direction D2, the width W2 of the narrow neck region R13 is greater than the width W3 of the diversion region R12, ensuring that the refrigerant flowing through the diversion region R12 can smoothly converge and accelerate in the narrow neck region R13. For example, along the second direction D2, the width W2 of the narrow neck region R13 is 7 mm, and the width W3 of the diversion region R12 is 5 mm.

[0061] In some embodiments, please refer to Figure 6 and combination Figure 8 The cross-sectional area of ​​the narrow neck region R13 is S1, and the cross-sectional area of ​​the diversion region R12 is S2, with S1:S2 = 2:1. The cross-sectional area of ​​the narrow neck region R13 is the area of ​​the cross-section obtained by the narrow neck region R13 through a plane perpendicular to the first direction D1, and the cross-sectional area of ​​the diversion region R12 is the area of ​​the cross-section obtained by the diversion region R12 through a plane perpendicular to the first direction D1. The cross-section obtained by the narrow neck region R13 through the plane perpendicular to the first direction D1 is approximately semi-circular, and the cross-sectional area S1 of the narrow neck region R13 is (π(W² / 2)). 2 / 2), the cross-section of the diversion region R12, which is cut by a plane perpendicular to the first direction D1, is also approximately semi-circular, and the cross-sectional area S2 of the diversion region R12 is (π(W3 / 2)). 2 / 2). Since a protruding structure 13 corresponds to two flow distribution areas R12, and S1:S2 = 2:1 is defined, it is equivalent to the sum of the cross-sectional areas of the two flow distribution areas R12 being equal to the cross-sectional area of ​​the narrow neck area R13. That is, the sum of the flow rates of the two flow distribution areas R12 is matched with the flow rate of the narrow neck area R13, ensuring that the refrigerant flowing through the flow distribution area R12 can be smoothly converged and accelerated in the narrow neck area R13.

[0062] In practical applications, S1:S2 = 2:1 means that the ratio of the cross-sectional area S1 of the narrow neck region R13 to the cross-sectional area S2 of the diversion region R12 is close to 2:1. For example, along the second direction D2, the width W2 of the narrow neck region R13 is 7 mm, the width W3 of the diversion region R12 is 5 mm, and the cross-sectional area S1 of the narrow neck region R13 is (π(W2 / 2)). 2 / 2) = (π(7 / 2)) 2 / 2) = 19.2mm 2 The cross-sectional area S2 of the diversion region R12 is (π(W3 / 2)). 2 / 2) = (π(5 / 2)) 2 / 2) = 9.8mm 2 .

[0063] Please continue reading. Figure 6 For the protruding structure 13, the outline of the protruding structure 13 obtained by the cross section parallel to the mounting part 11 is approximately circular. The diameter of this circular outline corresponds to the diameter D of the protruding structure 13. When the diameter D of the protruding structure 13 is small, it is beneficial for the refrigerant to interact with the cooling plate 2 (e.g., Figure 5 The heat transfer between the protruding structure 13 and the refrigeration plate 2 (as shown in the figure) is affected. However, the diameter D of the protruding structure 13 is constrained by the width W3 of the diversion region R12 along the second direction D2. A larger W3 results in a smaller diameter D of the protruding structure 13, but a larger W3 will affect the diversion effect on the refrigerant, affecting the effect of the diversion region R12 in disrupting the laminar boundary layer and enhancing turbulence, thereby weakening the heat transfer performance. Therefore, the matching relationship between the diameter D and the width W3 of the protruding structure 13 needs to be comprehensively considered, taking into account both the refrigerant and the heat transfer between the refrigerant and the refrigeration plate 2 (as shown in the figure). Figure 5 The heat transfer between the two (as shown) and the turbulence and diversion effects of the protruding structure 13 and the diversion area R12 on the refrigerant optimize the heat exchange efficiency.

[0064] It is worth noting that, please continue reading... Figure 6Due to the aforementioned first region R11, diversion region R12, and narrow neck region R13, the width of the flow channel R along the second direction D2 is not a fixed value, but rather varies in width. When determining the flow area of ​​the flow channel R, it is approximated by multiplying the length of the flow channel R by its width. The length of the flow channel R is the length of the flow channel R along its direction, and the width of the flow channel R is the average width of the flow channel R along the second direction D2, i.e., the weighted average of the widths of each region of the flow channel R along the second direction D2. To simplify the calculation, the width W2 of the narrow neck region R13 can be used as an approximate estimate of the width of the flow channel R. It can be understood that the flow area of ​​the flow channel R is the area between the flow channel R and the cooling plate 2 (e.g., ...). Figure 5 The effective heat exchange area between (as shown) is much larger than that in the prior art through pipe 101p (e.g. Figure 1 or Figure 2 (as shown) and cooling plate 20p (as shown) Figure 1 or Figure 2 The contact heat exchange area (as shown) allows for faster cooling of the evaporator 10 provided in this embodiment, provided the refrigerant flow rate is equal. Figure 5 The surface temperature (as shown) helps users prepare corresponding frozen dishes faster, shortens waiting time, and improves user experience.

[0065] Please see Figure 9 and combination Figure 4 and Figure 5 This utility model embodiment provides a refrigeration assembly 100, including a refrigeration plate 2 and an evaporator 10. The refrigeration plate 2 has a working surface 21 and a mounting surface 22 opposite to the working surface 21. The working surface 21 is used to pour liquid food and prepare frozen dishes. The mounting surface 22 is used to mount the evaporator 10. Specifically, the mounting part 11, the partition part 12, and the protruding structure 13 of the base plate 1 of the evaporator 10 are connected to the mounting surface 22 of the refrigeration plate 2 by means of bonding or welding. The refrigeration plate 2 closes the slot 1g of the receiving groove 1s of the base plate 1. For the specific structure and function of the evaporator 10, please refer to the foregoing content, which will not be repeated here. Through this refrigeration assembly 100, the refrigerant in the evaporator 10 directly contacts the mounting surface 22 of the refrigeration plate 2 for heat exchange. The heat transfer path is short, the heat loss during the heat transfer process is small, and the evaporator 10 has high refrigeration efficiency for the refrigeration plate 2.

[0066] It is worth noting that in some embodiments, the dimensions of the base plate 1 can be adapted to the mounting surface 22 of the cooling plate 2 to ensure full utilization of the refrigerant in the flow channel R in the base plate 1. Alternatively, as... Figure 4 As shown, the base plate 1 occupies approximately half of the mounting surface 22 of the refrigeration plate 2. Two evaporators 10 are installed for each refrigeration plate 2 to ensure sufficient cooling of the refrigeration plate 2.

[0067] It is worth noting that in some embodiments, the refrigeration assembly 100 further includes an inlet pipe 3 connected to the inlet 1a and an outlet pipe 4 connected to the outlet 1b. The arrangement of the inlet pipe 3 and the outlet pipe 4 facilitates the entry and exit of the refrigerant into and out of the flow channel R. It can be understood that when one refrigeration plate 2 corresponds to two evaporators 10, there are two inlet pipes 3 and two outlet pipes 4. One inlet pipe 3 and one outlet pipe 4 are respectively connected to the inlet 1a and outlet 1b of one evaporator 10.

[0068] Understandably, to accommodate the assembly tolerance requirements of inlet pipe 3 and inlet 1a, the outer diameter of inlet pipe 3 is smaller than the diameter of inlet 1a. For example, the outer diameter of inlet pipe 3 is 6mm, and the diameter of inlet 1a is 6.3mm. Similarly, to accommodate the assembly tolerance requirements of outlet pipe 4 and outlet 1b, the outer diameter of outlet pipe 4 is smaller than the diameter of outlet 1b. For example, the outer diameter of outlet pipe 4 is 6mm, and the diameter of outlet 1b is 6.3mm.

[0069] Please see Figure 10 This utility model embodiment also provides an ice food processor 1000, including a housing 5, a refrigeration system (not shown), an electronic control system (not shown), and a refrigeration assembly 100 disposed inside the housing 5; the electronic control system is connected to the refrigeration system, and the evaporator 10 in the refrigeration assembly 100 is connected to the refrigeration system. The refrigeration system is used to supply refrigerant to the evaporator 10, forming a closed refrigeration cycle. For the specific structure and function of the refrigeration assembly 100, please refer to the foregoing description, which will not be repeated here.

[0070] The function of a refrigeration system is to supply refrigerant. Refrigeration systems can be implemented in various ways. For example, a refrigeration system can use a compressor, condenser, throttling device, and evaporator 10 to form a vapor compression cycle system. Alternatively, it can be implemented using absorption or thermoelectric refrigeration methods. The specific method can be chosen according to actual needs, which will not be elaborated further here.

[0071] It should be noted that while the preferred embodiments of this utility model are provided in the specification and accompanying drawings, this utility model can be implemented in many different forms and is not limited to the embodiments described herein. These embodiments are not intended to impose additional limitations on the content of this utility model; their purpose is to provide a more thorough and comprehensive understanding of the disclosure of this utility model. Furthermore, the above-described technical features can be combined with each other to form various embodiments not listed above, all of which are considered to be within the scope of this utility model specification. Moreover, those skilled in the art can make improvements or modifications based on the above description, and all such improvements and modifications should fall within the protection scope of the appended claims.

Claims

1. An evaporator, characterized in that, include: Base plate; The base plate is recessed to form a receiving groove and a mounting part surrounding the receiving groove. The mounting part is used to connect to the refrigeration plate so that the refrigeration plate closes the opening of the receiving groove. The base plate is provided with an inlet and an outlet that connect the receiving slot; The bottom plate is recessed from the bottom of the receiving groove toward the opening of the receiving groove to form a partition, thereby forming a flow channel. The inlet and the outlet are respectively connected to the two ends of the flow channel.

2. The evaporator according to claim 1, characterized in that, The side of the mounting part facing away from the bottom of the receiving groove is flush with the side of the partition part facing away from the receiving groove, and the side of the partition part facing away from the receiving groove is used to connect to the refrigeration plate.

3. The evaporator according to claim 1, characterized in that, The partition includes a first section extending along a first direction. Along the first direction, the starting end of the first section is connected to the mounting portion, and there is a gap between the ending end of the first section and the mounting portion. Along a second direction perpendicular to the first direction, the first section and the mounting portion form a first part of the flow channel, the inlet is located in the first part, and the inlet is located near the area where the starting end of the first section is connected to the mounting portion; Along the second direction, the first section is recessed toward the first portion to form a protrusion; Along the second direction, a first region is formed between the protrusion and the mounting portion, and the first region is located near the inlet.

4. The evaporator according to claim 3, characterized in that, In the region corresponding to the flow channel, the bottom plate is recessed from the bottom of the receiving groove toward the opening of the receiving groove to form a raised structure and a diversion area. There are two diversion areas, which are arranged opposite to each other on both sides of the raised structure along the second direction.

5. The evaporator according to claim 4, characterized in that, The side of the protruding structure facing away from the receiving groove is flush with the side of the mounting part facing away from the bottom of the receiving groove, and the side of the protruding structure facing away from the receiving groove is used to connect to the refrigeration plate.

6. The evaporator according to claim 4, characterized in that, The flow channel has a narrow neck region.

7. The evaporator according to claim 6, characterized in that, The number of protruding structures is multiple, and the number of narrow neck regions is multiple. Along the direction of the flow channel, the protruding structures and the narrow neck regions are alternately arranged.

8. The evaporator according to claim 6, characterized in that, Along the first direction, the distance from the first region to the entrance is L, and the diameter of the entrance is d, where L > 5d; And / or, The width of the first region along the second direction is greater than the diameter of the entrance; And / or, Along the second direction, the width of the narrow neck region is greater than the width of the diversion region; And / or, The cross-sectional area of ​​the narrow neck region is S1, and the cross-sectional area of ​​the diversion region is S2, where S1:S2 = 2:

1.

9. A cooling component, characterized in that, It includes a refrigeration plate and an evaporator as described in any one of claims 1-8; the mounting part is connected to the refrigeration plate, and the refrigeration plate closes the opening of the receiving groove.

10. An ice food processor, characterized in that, It includes a housing, a refrigeration system, an electronic control system, and a refrigeration component as described in claim 9, all disposed within the housing; The electronic control system is connected to the refrigeration system, the inlet and the outlet are respectively connected to the refrigeration system, and the refrigeration system is used to supply refrigerant to the flow channel.

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