An evaporator for a snow melter

Abstract

The utility model discloses a kind of evaporators for snow melting machine, belong to evaporator technical field, including inner shell and shell, the circumferential between two of inner shell and shell has the flow channel that extends from head end to tail end in spiral shape, flow channel has the entrance for refrigerant inflow and the outlet for refrigerant outflow, flow channel includes first flow channel and second flow channel in double-end spiral shape distribution, entrance is located in the head end of first flow channel, outlet is located in the head end of second flow channel, the tail end of first flow channel is communicated with the tail end of second flow channel, refrigerant from entrance inflow flows through first flow channel and second flow channel in succession and then flows out from outlet. The flow direction of refrigerant in first flow channel is opposite to the flow direction in second flow channel, the refrigerant in first flow channel and the refrigerant in second flow channel superposition can balance the temperature of each point position on the axial direction of evaporator, improve the temperature uniformity of evaporator from head end to tail end, can greatly reduce the refrigeration effect difference of evaporator head and tail two ends.

Description

Technical Field

[0001] This utility model relates to the field of evaporator technology, and in particular to an evaporator for a snow melting machine. Background Technology

[0002] Snow melting machines, as a common beverage processing equipment, are widely used in the cold drink industry. Existing snow melting machines generally include a refrigeration system, a material tank, and a stirring device. The evaporator of the refrigeration system is located inside the material tank. The refrigerant flowing through the evaporator exchanges heat with the liquid in the material tank, cooling the liquid. The cooled liquid forms fine, dispersed ice crystals. The stirring rod of the stirring device, driven by a motor, rotates, stirs, and pushes the solid-liquid mixture in the material tank, causing the ice crystals to eventually form small-particle slush. A discharge nozzle is installed on the material tank, allowing the slush formed inside to be discharged through the open nozzle under the push of the stirring rod.

[0003] In an evaporator, the refrigerant flow channel typically extends spirally from the head end to the tail end, allowing the refrigerant to flow unidirectionally from the head to the tail end. Because the refrigerant absorbs heat through heat exchange during its flow, the temperature of the refrigerant at the head end of the evaporator is significantly lower than that at the tail end, resulting in a large temperature difference. This leads to a significant difference in cooling performance between the head and tail ends of the evaporator. Furthermore, since the head end of the evaporator is generally close to the discharge nozzle and the tail end is far from it, the material near the discharge nozzle in the hopper is prone to freezing, even deep freezing. This not only increases the stirring resistance of the stirring rod, significantly increasing the drive load on the motor, but can also freeze the discharge nozzle, preventing material from being discharged. Utility Model Content

[0004] To address the technical problem in the prior art where the large temperature difference between the two ends of the evaporator leads to a significant difference in cooling effect, this invention provides an evaporator for a snow melting machine. The first and second flow channels of the evaporator are distributed in a double-headed spiral pattern. The refrigerant flows in the opposite direction in the first and second flow channels. The superposition of the refrigerant in the first and second flow channels can balance the temperature at various points along the axial direction of the evaporator, improving the temperature uniformity of the evaporator from the head to the tail. This can greatly reduce the difference in cooling effect between the head and tail of the evaporator, thereby improving the effect of the evaporator's refrigerant liquid in forming slush.

[0005] To achieve the above-mentioned technical objectives, this utility model provides an evaporator for a snow melting machine, comprising an inner shell and an outer shell fitted outside the inner shell. A flow channel extending spirally from one end to the other is provided between the inner shell and the outer shell in the circumferential direction. The flow channel has an inlet for refrigerant to flow in and an outlet for refrigerant to flow out. The flow channel includes a first flow channel and a second flow channel distributed in a double-headed spiral pattern. The inlet is located at the first end of the first flow channel, and the outlet is located at the first end of the second flow channel. The tail ends of the first flow channel and the second flow channel are connected. Refrigerant flowing in from the inlet flows through the first flow channel and the second flow channel successively before flowing out from the outlet.

[0006] Preferably, the cross-sectional area of ​​the first flow channel gradually increases from the head end to the tail end.

[0007] Preferably, the cross-sectional area of ​​the second flow channel gradually decreases from the tail end to the head end.

[0008] Preferably, the spiral length of the second flow channel is greater than that of the first flow channel, so that the head end of the second flow channel is offset from the head end of the first flow channel in the circumferential direction.

[0009] Preferably, the tail end of the first flow channel and the tail end of the second flow channel are smoothly connected by an arc-shaped transition flow channel.

[0010] Preferably, the evaporator further includes an intermediate sleeve disposed circumferentially between the inner shell and the outer shell. The intermediate sleeve is provided with a double-headed spiral groove whose head ends are staggered and whose tail ends are connected. The outer circumferential surface of the inner shell, the inner circumferential surface of the outer shell, and the double-headed spiral groove cooperate to form a first flow channel and a second flow channel.

[0011] Preferably, the inner surface of the intermediate sleeve is bonded to the outer peripheral surface of the inner shell; and / or, the outer surface of the intermediate sleeve is bonded to the inner peripheral surface of the outer shell.

[0012] Preferably, the axial length of the inner shell is L1, the axial length of the intermediate sleeve is L2, and the axial inner length of the outer shell is L3, where L1 < L2 < L3.

[0013] Preferably, one end of the outer casing is open and the other end is closed, the inlet and the outlet are close to the closed end of the outer casing, and the evaporator includes an inlet pipe communicating with the inlet and an outlet pipe communicating with the outlet, the inlet pipe and the outlet pipe being staggered circumferentially.

[0014] Preferably, both the portion of the inlet tube and the portion of the outlet tube extend radially and have an included angle θ between them, where 15°≤θ≤180°.

[0015] By adopting the above technical solution, this utility model has the following advantages: 1. The evaporator for a snow melting machine provided by this utility model includes a first flow channel and a second flow channel distributed in a double-headed spiral shape between the inner shell and the outer shell. The inlet and outlet are respectively located at the head end of the first flow channel and the head end of the second flow channel. The tail end of the first flow channel and the tail end of the second flow channel are connected to each other. The refrigerant flowing in from the inlet flows through the first flow channel and the second flow channel in sequence and then flows out from the outlet. Because the first and second flow channels are arranged in a double-headed spiral pattern, the refrigerant flowing into the first flow channel from the inlet flows from the head to the tail, while the refrigerant flowing through the first flow channel flows from the tail to the head in the second flow channel and finally exits from the outlet. That is, the flow direction of the refrigerant in the first flow channel is opposite to that in the second flow channel. Furthermore, because the refrigerant gradually heats up during flow due to heat absorption, the temperature of the refrigerant in the first flow channel gradually increases from the head to the tail, meaning the cooling intensity of the refrigerant on the external liquid in the first flow channel gradually decreases from the head to the tail. Similarly, the temperature of the refrigerant in the second flow channel gradually increases from the tail to the head, meaning the cooling intensity of the refrigerant on the external liquid in the second flow channel gradually decreases from the tail to the head. The superposition of refrigerant in the second flow channel balances the temperature at various points along the evaporator's axial direction, improving temperature uniformity from head to tail and significantly reducing temperature differences between the two ends. This greatly reduces the difference in cooling effect between the two ends, preventing the external liquid at the head of the evaporator from easily freezing or even deeply freezing due to a large temperature difference. This enhances the evaporator's ability to cool the external liquid, forming slush. It also reduces the stirring resistance of the agitator in the snow melting machine, thus reducing the drive load on the motor and preventing overheating and burnout. This ensures motor performance stability and prevents the discharge nozzle from freezing and preventing slush from being discharged. Furthermore, because the first and second flow channels adopt a double-headed spiral distribution, their respective leads are significantly increased compared to existing single-spiral flow channels. This allows the refrigerant flowing in from the inlet to quickly distribute throughout the evaporator, further improving temperature uniformity from head to tail.

[0016] 2. As the refrigerant flows from the head to the tail end of the first flow channel, it absorbs heat and expands. Preferably, the cross-sectional area of ​​the first flow channel gradually increases from the head to the tail end. The smaller cross-sectional area at the head end restricts the expansion space of the refrigerant, thus appropriately reducing the heat absorption effect of refrigerant vaporization at the head end of the first flow channel. This reduces or prevents the external liquid being cooled from becoming too cold and easily freezing or even deeply freezing due to excessive heat absorption by the refrigerant at the head end. Furthermore, because the cross-sectional area of ​​the first flow channel gradually increases from the head to the tail end, the refrigerant can gradually absorb heat and expand as it flows. This change in the cross-sectional area improves the uniformity of heat absorption as the refrigerant flows through the first flow channel, thereby helping to reduce the difference in cooling effect between the head and tail ends of the evaporator. Additionally, since a smaller cross-sectional area results in a faster flow velocity, the smaller cross-sectional area at the head end allows the refrigerant to flow more quickly to the tail end of the first flow channel.

[0017] 3. As the refrigerant flows from the tail end to the head end in the second flow channel, it will gradually absorb heat and expand. The flow cross-sectional area of ​​the second flow channel is preferably gradually reduced from the tail end to the head end. By limiting the space for the refrigerant to absorb heat and expand when it flows in the second flow channel, the cooling intensity of the refrigerant to the external liquid in the second flow channel can be further gradually reduced from the tail end to the head end. Since the cooling intensity of the refrigerant to the external liquid in the first flow channel gradually decreases from the head end to the tail end, the superposition of the cooling intensity of the refrigerant in the two flow channels can reduce the difference in cooling effect at various points along the axial direction of the evaporator, thereby improving the cooling uniformity of the evaporator from the head end to the tail end.

[0018] 4. The spiral length of the second flow channel is preferably greater than that of the first flow channel. This allows the head end of the second flow channel to be offset from the head end of the first flow channel by a certain distance in the circumferential direction of the evaporator. Since there is a large temperature difference between the refrigerant flowing into the head end of the first flow channel from the inlet and the refrigerant flowing from the head end of the second flow channel to the outlet, the extra spiral length of the second flow channel appropriately increases the flow path length of the heat-absorbing and temperature-raising refrigerant at the head end of the second flow channel. This better balances the cooling intensity of the low-temperature refrigerant flowing into the head end of the first flow channel from the inlet, and avoids the situation where the external liquid is easily overcooled due to excessive cooling at the head end of the evaporator, resulting in icing or even freezing.

[0019] 5. Preferably, the tail ends of the first and second flow channels are smoothly connected by an arc-shaped transition flow channel. The arc-shaped transition flow channel allows the flow cross-sectional area between the tail ends of the first and second flow channels to remain constant or change only slightly, avoiding the formation of abrupt changes in flow cross-sectional area at the tail ends of the first and second flow channels. This prevents the formation of supercooling points at the connection point of the two flow channels due to the abrupt change in flow cross-sectional area, and thus avoids the evaporator from easily freezing or even icing due to supercooling at the connection point of the two flow channels. This not only appropriately reduces the stirring resistance of the snow melting machine's stirring device, but also appropriately reduces stirring noise.

[0020] 6. The evaporator also includes an intermediate sleeve, which is located circumferentially between the inner shell and the outer shell. The intermediate sleeve has double-headed spiral grooves with staggered ends and interconnected tail ends. The first and second flow channels are formed by the cooperation of the outer circumferential surface of the inner shell, the inner circumferential surface of the outer shell, and the double-headed spiral grooves. A well-designed structure for the first and second flow channels reduces the difficulty of their formation, as well as the structural and assembly complexity of the evaporator. Since the inner circumferential surface of the outer shell forms the inner wall of the flow channels, the refrigerant can directly contact the outer shell, which helps improve the evaporator's cooling effect on external liquids.

[0021] 7. The inner surface of the intermediate sleeve is preferably bonded to the outer circumferential surface of the inner shell to maintain a sealed fit. The outer surface of the intermediate sleeve is preferably bonded to the inner circumferential surface of the outer shell to maintain a sealed fit. By rationally designing the sealing fit methods between the intermediate sleeve and the inner and outer shells, the difficulty of sealing is reduced while ensuring the effectiveness of the sealing fit. This allows the first and second flow channels to remain relatively independent, preventing refrigerant cross-flow between the first and second flow channels, and ensuring that the refrigerant completely flows through the first flow channel before entering the second flow channel.

[0022] 8. Reasonably set the axial length L1 of the inner shell, the axial length L2 of the intermediate sleeve, and the axial inner length L3 of the outer shell to ensure sufficient weld space between the ends of the inner shell and the intermediate sleeve, as well as between the ends of the intermediate sleeve and the outer shell. This ensures the welding effect of the inner shell, intermediate sleeve, and outer shell and prevents refrigerant leakage from the weld seam in the flow channel.

[0023] 9. The outer casing is open at one end and closed at the other. The inlet and outlet are located near the closed end of the casing, allowing the inlet and outlet pipes to be inserted from the open end for easy assembly. The inlet and outlet pipes are preferably staggered circumferentially for easy fixation.

[0024] 10. Both the inlet and outlet pipes extend radially along the evaporator. A well-designed structure for the inlet and outlet pipes reduces the difficulty of fitting the inlet pipe to the inlet and outlet, improving the smoothness of refrigerant flow from the inlet to the inlet and from the outlet to the outlet. A well-designed angle θ between the radially extending portions of the inlet and outlet pipes provides sufficient welding space, reducing welding difficulty. If θ is less than 15°, the inlet and outlet pipes are too close, resulting in less welding space, increased welding difficulty, and compromised welding quality. If θ is greater than 180°, the inlet and outlet pipes are too far apart, leading to a greater distance between the inlet and outlet, which is detrimental to maintaining temperature equilibrium between the refrigerant at the inlet and outlet. Attached Figure Description

[0025] Figure 1 This is a perspective view of the evaporator in Example 1; Figure 2 This is an exploded view of the evaporator in Example 1; Figure 3 This is a cross-sectional view of the evaporator along the axial direction in Example 1; Figure 4 for Figure 3 Schematic diagram of the weld at point A; Figure 5 for Figure 3 Schematic diagram of the weld at point B; Figure 6 This is a structural diagram of the intermediate sleeve in Example 1; Figure 7 This is a schematic diagram of the intermediate sleeve unfolding circumferentially in Example 1; Figure 8 This is a schematic diagram showing the evaporator flow channel in Example 1 unfolded circumferentially; Figure 9 This is a side view of the tail end of the evaporator in Example 1; Figure 10 This is a perspective view of the snow melting machine in Example 1; Figure 11 This is a diagram of the internal structure of the snow melting machine in Example 1.

[0026] In the diagram, 100-evaporator, 110-inner shell, 120-outer shell, 120a-closed end, 120b-open end, 121-end cap, 122-protruding flange, 130-intermediate sleeve, 131-double-headed spiral groove, 1311-first spiral groove, 1312-second spiral groove, 1313-arc groove, 140-flow channel, 141-first flow channel, 142-second flow channel, 143-transition flow channel, 144-inlet, 145-outlet, 151-weld I, 152-weld II, 153-weld III, 160-inlet pipe, 161-first pipe section, 162-second pipe section, 170-outlet pipe, 171-third pipe section, 172-fourth pipe section. 200 - Main unit, 210 - Chassis, 220 - Cooling system 300 - Material barrel, 310 - Cover, 410 - Discharge nozzle, 420 - Handle 500 - Stirring rod. Detailed Implementation

[0027] The present invention will be further described below with reference to the accompanying drawings and specific embodiments. It should be understood that the terms "upper," "lower," "left," "right," "longitudinal," "lateral," "inner," "outer," "vertical," "horizontal," "top," and "bottom," etc., which indicate orientation or positional relationship, are based solely on the orientation or positional relationship shown in the accompanying drawings and are used only for the convenience of describing the present invention and simplifying the description. They do not indicate or imply that the device / component referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present invention. Example

[0028] Combination Figures 1 to 9 The present invention provides an evaporator 100 for a snow melting machine, comprising an inner shell 110 and an outer shell 120 sleeved outside the inner shell 110. A flow channel 140 extending spirally from one end to the other is provided circumferentially between the inner shell 110 and the outer shell 120. The flow channel 140 has an inlet 144 for refrigerant to flow in and an outlet 145 for refrigerant to flow out. The flow channel 140 includes a first flow channel 141 and a second flow channel 142 arranged in a double-headed spiral. The inlet 144 is located at the first end of the first flow channel 141, and the outlet 145 is located at the first end of the second flow channel 142. The tail ends of the first flow channel 141 and the second flow channel 142 are connected. Refrigerant flowing in from the inlet 144 flows through the first flow channel 141 and the second flow channel 142 successively before flowing out from the outlet 145.

[0029] Because the first flow channel 141 and the second flow channel 142 are arranged in a double-headed spiral pattern, the refrigerant flowing into the first flow channel 141 from the inlet 144 flows from the head end to the tail end, and the refrigerant flowing through the first flow channel 141 flows from the tail end to the head end in the second flow channel 142 and finally flows out from the outlet 145. That is, the flow direction of the refrigerant in the first flow channel 141 is opposite to the flow direction in the second flow channel 142. Furthermore, because the refrigerant will gradually increase in temperature due to heat absorption during the flow, the temperature of the refrigerant in the first flow channel 141 gradually increases from the head end to the tail end, meaning that the cooling intensity of the refrigerant in the first flow channel 141 on the external liquid gradually decreases from the head end to the tail end. Similarly, the temperature of the refrigerant in the second flow channel 142 gradually increases from the tail end to the head end, meaning that the cooling intensity of the refrigerant in the second flow channel 142 on the external liquid gradually decreases from the tail end to the head end. The refrigerant in flow channel 141 and the refrigerant in the second flow channel 142 can balance the temperature at various points along the axial direction of the evaporator 100, improve the temperature uniformity of the evaporator 100 from the head to the tail, and greatly reduce the temperature difference between the head and tail of the evaporator 100. This greatly reduces the difference in cooling effect between the head and tail of the evaporator 100, and avoids the situation where the external liquid at the head of the evaporator 100 is prone to freezing or even deep freezing due to a large temperature difference between the two ends of the evaporator 100. This improves the effect of the refrigerant liquid in the evaporator 100 forming ice slush. It can also reduce the stirring resistance of the stirring device in the snow melting machine, thereby reducing the drive load of the stirring device motor and preventing the stirring device motor from overheating and burning out due to a large drive load. This ensures the performance stability of the motor and also prevents the discharge nozzle of the snow melting machine from freezing and preventing the ice slush from being discharged. In addition, since the first flow channel 141 and the second flow channel 142 adopt a double-headed spiral distribution, the lead of each of the first flow channel 141 and the second flow channel 142 is significantly increased compared with the existing single spiral flow channel. This allows the refrigerant flowing in from the inlet 144 to be quickly distributed throughout the evaporator 100, which helps to improve the temperature uniformity of the evaporator 100 from the head end to the tail end.

[0030] In this embodiment, when the evaporator 100 is applied to the snow melting machine, the end facing the discharge nozzle is defined as the head end (or front end), and the end away from the discharge nozzle is defined as the tail end (or rear end).

[0031] Combination Figure 2 , Figure 6In this embodiment, the evaporator 100 further includes an intermediate sleeve 130, which is disposed circumferentially between the inner shell 110 and the outer shell 120, i.e., the inner shell 110, intermediate sleeve 130, and outer shell 120 are sequentially fitted together from the inside out. The intermediate sleeve 130 is provided with a double-headed spiral groove 131. The outer circumferential surface of the inner shell 110, the inner circumferential surface of the outer shell 120, and the double-headed spiral groove 131 on the intermediate sleeve 130 cooperate to form a first flow channel 141 and a second flow channel 142. The reasonable arrangement of the formation structure of the first flow channel 141 and the second flow channel 142 facilitates the reduction of formation difficulty and also reduces the structural and assembly difficulty of the evaporator 100. Since the inner circumferential surface of the outer shell 120 forms the inner wall of the flow channel 140, the refrigerant can directly contact the outer shell 120, which helps to improve the cooling effect of the evaporator 100 on external liquids.

[0032] Specifically, the inner shell 110, the intermediate sleeve 130, and the outer shell 120 are all roughly hollow cylindrical in shape, combined with Figure 7 The double-headed spiral groove 131 on the intermediate sleeve 130 includes a first spiral groove 1311 and a second spiral groove 1312. Both the first spiral groove 1311 and the second spiral groove 1312 extend spirally from the head end of the intermediate sleeve 130 around the central axis X of the intermediate sleeve 130 to the tail end of the intermediate sleeve 130. Figure 7 The solid line represents the first helical groove 1311, and the dashed line represents the second helical groove 1312. The axial extension areas of the two helical grooves roughly overlap. A certain distance is maintained between the beginning and end ends of the first helical groove 1311 and the corresponding end faces of the intermediate sleeve 130. A certain distance is also maintained between the beginning and end ends of the second helical groove 1312 and the corresponding end faces of the intermediate sleeve 130. The lead S1 of the first helical groove 1311 is the same as the lead S2 of the second helical groove 1312. The pitch between any two adjacent turns on the double-ended helical groove 131 is the same and is P, where S1 = S2 = 2 × P. That is, the parameters of the first helical groove 1311 and the second helical groove 1312 are the same and are axially offset by 1 / 2 × S1 (or 1 / 2 × S2).

[0033] Furthermore, the helical length of the second helical groove 1312 is slightly greater than that of the first helical groove 1311, causing the beginnings of the first helical groove 1311 and the second helical groove 1312 to be offset circumferentially by a certain distance. Specifically, the beginning of the second helical groove 1312 extends forward helically by a certain distance ΔD relative to the beginning of the first helical groove 1311. Thus, the distance between the beginnings of the two helical grooves in the circumferential direction of the intermediate sleeve 130 is D1, and the distance between the beginnings of the two helical grooves in the axial direction is D2. Because the beginnings of the two helical grooves are offset circumferentially by a certain distance from the intermediate sleeve 130, the radial directions corresponding to the endpoints of the beginnings of the two helical grooves are also different, that is, the starting phases of the beginnings of the two helical grooves relative to the intermediate sleeve 130 in the circumferential direction are different. Furthermore, the tail end of the first spiral groove 1311 and the tail end of the second spiral groove 1312 are preferably connected by an arc-shaped groove 1313, one end of the arc-shaped groove 1313 is smoothly connected to the tail end of the first spiral groove 1311, and the other end of the arc-shaped groove 1313 is smoothly connected to the tail end of the second spiral groove 1312.

[0034] Combination Figure 8 Since the first flow channel 141 and the second flow channel 142 are formed by the cooperation of the outer peripheral surface of the inner shell 110, the double-headed spiral groove 131 on the intermediate sleeve 130, and the inner peripheral surface of the outer shell 120, the first flow channel 141 and the second flow channel 142 are also double-headed spirals. That is, both the first flow channel 141 and the second flow channel 142 extend spirally from the head end of the evaporator 100 around the central axis of the evaporator 100 to the tail end of the evaporator 100. The spiral extension areas of the first flow channel 141 and the second flow channel 142 in the axial direction roughly overlap, and the leads of the first flow channel 141 and the second flow channel 142 are the same. Figure 8 The solid line in the diagram represents the first flow channel 141, and the dashed line represents the second flow channel 142. Since the head end of the second spiral groove 1312 extends forward spirally a certain distance relative to the head end of the first spiral groove 1311, the head end of the second flow channel 142 also extends forward spirally a certain distance relative to the head end of the first flow channel 141, so that the head ends of the second flow channel 142 and the head ends of the first flow channel 141 are offset circumferentially. Because the refrigerant flowing from inlet 144 into the head end of the first flow channel 141 has a large temperature difference with the refrigerant flowing from the head end of the second flow channel 142 to the outlet 145, the spiral length that extends forward from the head end of the second flow channel 142 relative to the head end of the first flow channel 141 can appropriately increase the flow path length of the heat-absorbing and temperature-raising refrigerant at the head end of the second flow channel 142. This better balances the cooling intensity of the low-temperature refrigerant flowing from inlet 144 into the head end of the first flow channel 141, and avoids the situation where the external liquid is easily overcooled due to excessive cooling at the head end of the evaporator 100, resulting in icing or even freezing.

[0035] In this embodiment, the arc-shaped groove 1313 at the tail end of the double-headed spiral groove 131 cooperates with the outer peripheral surface of the inner shell 110 and the inner peripheral surface of the outer shell 120 to form a transition channel 143 for connecting the tail end of the first flow channel 141 and the tail end of the second flow channel 142. The transition channel 143 is arc-shaped, one end of the transition channel 143 is smoothly connected to the tail end of the first flow channel 141, and the other end of the transition channel 143 is smoothly connected to the tail end of the second flow channel 142. The arc-shaped transition channel 143 allows the flow cross-sectional area between the tail end of the first flow channel 141 and the tail end of the second flow channel 142 to remain constant or change only slightly, avoiding the formation of abrupt changes in flow cross-sectional area at the tail end of the first flow channel 141 and the tail end of the second flow channel 142. This prevents the formation of supercooling points at the connection point of the two flow channels due to abrupt changes in flow cross-sectional area, and further prevents the evaporator 100 from easily freezing or even icing due to supercooling at the connection point of the two flow channels. This not only appropriately reduces the stirring resistance of the snow melting machine's stirring device, but also appropriately reduces stirring noise.

[0036] like Figure 8 As shown, in this embodiment, the first flow channel 141 extends spirally from the head end to the tail end and includes several turns as shown by a, b, c, d, e, and f, which are distributed sequentially from the head end to the tail end. The second flow channel 142 extends spirally from the head end to the tail end and includes several turns as shown by g, h, j, k, m, and n, which are distributed sequentially from the tail end to the head end. The f turns of the first flow channel 141 and the g turns of the second flow channel 142 are connected by a transition flow channel 143. In this embodiment, as a preferred embodiment, the flow cross-sectional area of ​​the first flow channel 141 gradually increases from the head end to the tail end. Specifically, the flow cross-sectional area of ​​the first flow channel 141 refers to the cross-sectional area of ​​the first flow channel 141 along the direction perpendicular to the refrigerant flow. Since the height of the first flow channel 141 remains constant from the head end to the tail end, the width of the first flow channel 141 gradually increases from the head end to the tail end. The width of the first flow channel 141 at the head end is W11, and the width at the tail end is W12, where W11 < W12. During the process of the refrigerant flowing from the head end to the tail end in the first flow channel 141, it will absorb heat and expand. The preferred flow cross-sectional area of ​​the first flow channel 141 gradually increases from the head end to the tail end. The smaller flow cross-sectional area at the head end can limit the expansion space of the refrigerant, thereby appropriately weakening the effect of refrigerant vaporization and heat absorption at the head end of the first flow channel 141. This reduces or avoids the situation where the external liquid being cooled is too cold and easily freezes or even deeply freezes due to the refrigerant absorbing more heat at the head end of the first flow channel 141. Furthermore, since the flow cross-sectional area of ​​the first flow channel 141 gradually increases from the head end to the tail end, the refrigerant can gradually absorb heat and expand as it flows from the head end to the tail end within the first flow channel 141. This variation in the flow cross-sectional area of ​​the first flow channel 141 improves the uniformity of heat absorption as the refrigerant flows through it, thereby helping to reduce the difference in cooling effect between the head and tail ends of the evaporator 100. Additionally, since a smaller flow cross-sectional area results in a faster flow velocity, a smaller flow cross-sectional area at the head end allows the refrigerant to flow more quickly to the tail end of the first flow channel 141. In an alternative embodiment, the flow cross-sectional area of ​​the first flow channel 141 can also be kept constant from the head end to the tail end; in this case, the width W11 at the head end of the first flow channel 141 is the same as the width W12 at the tail end.

[0037] In this embodiment, as a preferred option, the flow cross-sectional area of ​​the second flow channel 142 gradually decreases from the tail end to the head end. Specifically, the flow cross-sectional area of ​​the second flow channel 142 refers to the cross-sectional area of ​​the second flow channel 142 along the direction perpendicular to the refrigerant flow. Since the height of the second flow channel 142 remains constant from the tail end to the head end, the width of the second flow channel 142 gradually decreases from the tail end to the head end. The width of the second flow channel 142 at the head end is W21, and the width at the tail end is W22, where W21 < W22. As the refrigerant flows from the tail end to the head end within the second flow channel 142, it gradually absorbs heat and expands. Preferably, the flow cross-sectional area of ​​the second flow channel 142 gradually decreases from the tail end to the head end. This change in flow cross-sectional area restricts the space for heat absorption and expansion of the refrigerant during its flow within the second flow channel 142, further reducing the cooling intensity of the refrigerant on the external liquid from the tail end to the head end. Since the cooling intensity of the refrigerant on the external liquid in the first flow channel 141 gradually decreases from the head end to the tail end, the combined cooling intensity of the refrigerant in the two flow channels can reduce the difference in cooling effect at various points along the axial direction of the evaporator 100, thereby improving the cooling uniformity of the evaporator 100 from the head end to the tail end. In an alternative embodiment, the flow cross-sectional area of ​​the second flow channel 142 can also be kept constant from the tail end to the head end. In this case, the width W22 at the tail end of the second flow channel 142 is the same as the width W21 at the head end.

[0038] The flow cross-sectional area of ​​the transition channel 143 at the end connected to the first channel 141 is preferably the same as the flow cross-sectional area of ​​the first channel 141 at the tail end. Similarly, the flow cross-sectional area of ​​the transition channel 143 at the end connected to the second channel 142 is preferably the same as the flow cross-sectional area of ​​the second channel 142 at the tail end. The width W12 of the first channel 141 at the tail end and the width W22 of the second channel 142 at the tail end can be the same. In this case, the flow cross-sectional area of ​​the first channel 141 at the tail end and the flow cross-sectional area of ​​the second channel 142 at the tail end are the same. The flow cross-sectional area of ​​the transition channel 143 remains consistent from the end connected to the tail end of the first channel 141 to the end connected to the tail end of the second channel 142, thus ensuring a smooth connection between the two ends of the transition channel 143 and the tail ends of the first channel 141 and the second channel 142, respectively. In other embodiments of this invention, the width W22 of the second flow channel 142 at the tail end can also be slightly larger than the width W12 of the first flow channel 141 at the tail end. In this case, the width of the transition flow channel 143 gradually increases from the end connected to the tail end of the first flow channel 141 to the other end connected to the tail end of the second flow channel 142. That is, the flow cross-sectional area of ​​the transition flow channel 143 gradually increases from the end connected to the tail end of the first flow channel 141 to the other end connected to the tail end of the second flow channel 142.

[0039] To prevent cross-flow of refrigerant in the first flow channel 141 and the second flow channel 142, in this embodiment, the inner surface of the intermediate sleeve 130 is bonded to the outer peripheral surface of the inner shell 110, and the outer surface of the intermediate sleeve 130 is bonded to the inner peripheral surface of the outer shell 120. By bonding, the inner surface of the intermediate sleeve 130 and the outer peripheral surface of the inner shell 110 can maintain a sealed fit, and the outer surface of the intermediate sleeve 130 and the inner peripheral surface of the outer shell 120 can also maintain a sealed fit. As a result, the first flow channel 141 and the second flow channel 142 are both circumferentially sealed, and the refrigerant can only flow along the extension direction of the flow channel. In order to bond the inner surface of the intermediate sleeve 130 to the outer peripheral surface of the inner shell 110, adhesive can be applied to the outer peripheral surface of the inner shell 110 and / or the inner surface of the intermediate sleeve 130 and allowed to evaporate to a "finger-dry" state (not sticky to the touch but still tacky). Then, the inner shell 110 and the intermediate sleeve 130 are fitted together. After the adhesive is completely dry, the outer peripheral surface of the inner shell 110 and the inner surface of the intermediate sleeve 130 are bonded together, thereby achieving a sealing fit between the outer peripheral surface of the inner shell 110 and the inner surface of the intermediate sleeve 130. To bond the outer surface of the intermediate sleeve 130 to the inner circumferential surface of the outer shell 120, adhesive can be applied to the inner circumferential surface of the outer shell 120 and / or the outer surface of the intermediate sleeve 130 and allowed to evaporate to a "finger-dry" state (not sticky to the touch but still tacky). Then, the intermediate sleeve 130 is fitted onto the outer shell 120. After the adhesive has completely dried, the inner circumferential surface of the outer shell 120 is bonded to the outer surface of the intermediate sleeve 130, thus achieving a sealed fit between the inner circumferential surface of the outer shell 120 and the outer surface of the intermediate sleeve 130. Of course, the fitting method between the inner shell 110 and the intermediate sleeve 130, or between the intermediate sleeve 130 and the outer shell 120, is not limited to the aforementioned bonding method; other methods can also achieve a sealed fit.

[0040] In this embodiment, the outer casing 120 has a closed head end and an open tail end. Specifically, the outer casing 120 has an end cap 121 at its head end, which forms a closed head end 120a and an open tail end 120b. The outer casing 120 also has a radially outward protruding flange 122 at its tail end. The inner shell 110, outer casing 120, and intermediate sleeve 130 can all be made of metal. In this case, to ensure the structural stability of the evaporator 100, the components of the evaporator 100 can be fixed together by welding. Figure 3To ensure welding quality, in this embodiment, the axial length of the inner shell 110 is L1, the axial length of the intermediate sleeve 130 is L2, and the axial inner length of the outer shell 120 is L3, where L1 < L2 < L3. By rationally setting the relationship between the axial lengths L1 of the inner shell 110, L2 of the intermediate sleeve 130, and L3 of the outer shell 120, sufficient weld space is provided between the ends of the inner shell 110 and the intermediate sleeve 130, as well as between the ends of the intermediate sleeve 130 and the outer shell 120. This ensures the welding effect of the inner shell 110, intermediate sleeve 130, and outer shell 120, and prevents refrigerant leakage from the weld seams within the flow channel 140. The axial inner length L3 of the outer shell 120 refers to the axial length of the hollow cavity formed by the outer shell 120. Specifically, in conjunction with… Figure 4 The head end of the intermediate sleeve 130 and the head end of the inner shell 110 can be aligned and both abut against the end cap 121 at the head end of the outer shell 120, thereby achieving axial positioning of the intermediate sleeve 130 and the inner shell 110 during assembly. The inner side of the head end of the inner shell 110 is welded to the end cap 121 to form weld I 151. Figure 5 Since the axial lengths of the inner shell 110, intermediate sleeve 130, and outer shell 120 increase sequentially, the tail end of the intermediate sleeve 130 protrudes backward a short distance relative to the tail end of the inner shell 110. That is, the inner surface of the intermediate sleeve 130 protrudes backward a short distance relative to the tail end face of the inner shell 110. Welding can be performed between the tail end face of the inner shell 110 and the inner surface of the tail end of the intermediate sleeve 130 to form weld II 152. The tail end of the outer shell 120 protrudes backward a short distance relative to the tail end of the intermediate sleeve 130. That is, the inner circumferential surface of the outer shell 120 protrudes backward a short distance relative to the tail end face of the intermediate sleeve 130. Welding can be performed between the tail end face of the intermediate sleeve 130 and the inner circumferential surface of the tail end of the outer shell 120 to form weld III 153. Of course, the inner shell 110, outer shell 120 and intermediate sleeve 130 of the evaporator 100 can also be fixed in other ways. Here, the fixing method between the components of the evaporator 100 is not strictly limited.

[0041] In this embodiment, the evaporator 100 further includes an inlet pipe 160 communicating with the inlet 144 and an outlet pipe 170 communicating with the outlet 145. The inlet pipe 160 and the outlet pipe 170 are staggered along the circumference of the evaporator 100. The inner shell 110 is provided with a clearance hole at a position corresponding to the inlet 144. One end of the inlet pipe 160 is fixed to the inner shell 110, thereby connecting the inlet pipe 160 to the inlet 144. The inner shell 110 is also provided with a clearance hole at a position corresponding to the outlet 145. One end of the outlet pipe 170 is fixed to the inner shell 110, thereby connecting the outlet pipe 170 to the outlet 145. The inlet pipe 160 and the outlet pipe 170 can be made of metal. In this case, both the inlet pipe 160 and the outlet pipe 170 can be fixedly connected to the inner shell 110 by welding. Furthermore, the inlet pipe 160 includes a first pipe section 161 and a second pipe section 162 that are generally L-shaped, and the outlet pipe 170 includes a third pipe section 171 and a fourth pipe section 172 that are generally L-shaped. The inlet pipe 160, which is fixedly connected to the inner shell 110, arranges the first pipe section 161 generally along the axial direction of the inner shell 110 and arranges the second pipe section 162 generally along the radial direction of the inner shell 110. The outlet pipe 170, which is fixedly connected to the inner shell 110, arranges the third pipe section 171 generally along the axial direction of the inner shell 110 and arranges the fourth pipe section 172 generally along the radial direction of the inner shell 110. The first pipe section 161 of the inlet pipe 160 and the third pipe section 171 of the outlet pipe 170 are generally parallel and separated by a certain distance. Since the second pipe section 162 and the fourth pipe section 172 are arranged approximately along the radial direction of the inner shell 110, it is easier to reasonably reduce the difficulty of matching between the inlet pipe 160 and the inlet 144, and also easier to reasonably reduce the difficulty of matching between the outlet pipe 170 and the outlet 145, thereby improving the smoothness of refrigerant flow from the inlet pipe 160 to the inlet 144 and the smoothness of refrigerant flow from the outlet 145 to the outlet pipe 170.

[0042] Combination Figure 9 To reduce the welding difficulty of the inlet pipe 160 and the outlet pipe 170, an angle θ is formed between the second section 162 of the inlet pipe 160 and the fourth section 172 of the outlet pipe 170, where 15°≤θ≤180°. This appropriately sized angle θ provides sufficient welding space between the inlet pipe 160 and the outlet pipe 170. Specifically, in this embodiment, the angle θ is approximately 120°. In an alternative embodiment, the included angle θ can also be set to other reasonable values ​​such as 15°, 20°, 25°, 30°, 35°, 40°, 45°, 50°, 55°, 60°, 65°, 70°, 75°, 80°, 85°, 90°, 95°, 100°, 105°, 110°, 115°, 119°, 122°, 125°, 130°, 135°, 140°, 145°, 150°, 155°, 160°, 165°, 170°, 175°, 180°, etc.

[0043] Combination Figure 10 , Figure 11 This embodiment also provides a snow melting machine, which includes a main unit 200 and a material cylinder 300. The material cylinder 300 is mounted on the main unit 200. The top side of the material cylinder 300 is provided with a feeding port and a cover 310 for opening and closing the feeding port. The cover 310 can be hinged to the material cylinder 300 or slidably mounted on the material cylinder 300. Of course, the cover 310 can also be mounted on the material cylinder 300 in other openable and closable ways. The mounting method of the cover 310 is not specifically limited here. The front end of the material cylinder 300 is provided with a discharge nozzle 410 and a lever 420 for opening and closing the discharge nozzle 410. The structure of the discharge nozzle 410 and the lever 420 can refer to the prior art, and will not be described in detail here. The evaporator 100 described above is positioned inside the material cylinder 300 and is axially transverse, with the head end of the evaporator 100 facing forward and the tail end facing backward. An agitator 500 is fitted around the outside of the evaporator 100. A motor for driving the agitator 500 can be installed inside the main unit 200. A transmission structure is provided between the output shaft of the motor and the agitator 500. The motor can drive the agitator 500 to rotate around its own central axis through the transmission structure. The structure by which the motor drives the agitator 500 to rotate can refer to the prior art, and will not be described in detail here.

[0044] The main unit 200 includes a housing 210 and a cooling system 220 disposed within the housing 210. The cooling system 220 cools the refrigerant. The cooled refrigerant flows into the flow channel 140 through the inlet pipe 160. The refrigerant flowing through the flow channel 140 returns to the cooling system 220 through the outlet pipe 170 and is cooled again. This process repeats, allowing the refrigerant flowing through the flow channel 140 to continuously exchange heat with the liquid in the barrel 300, thereby enabling the liquid in the barrel 300 to form fine and dispersed ice slush. The cooling system 220 can refer to existing technology and will not be described in detail here.

[0045] Combination Figure 8In this embodiment, the refrigerant, which is cooled by the cooling system 220 and has a lower temperature, flows into the head end of the first flow channel 141 through the inlet pipe 160 from the inlet 144. The refrigerant flowing into the first flow channel 141 flows from the head end to the tail end in the direction shown by the solid arrows a→b→c→d→e→f. The refrigerant flowing to the tail end of the first flow channel 141 flows to the tail end of the second flow channel 142 through the transition flow channel 143. The refrigerant flowing into the second flow channel 142 flows from the tail end to the head end in the direction shown by the dashed arrows g→h→j→k→m→n. The refrigerant flowing to the head end of the second flow channel 142 flows from the outlet 145 to the outlet pipe 170. The refrigerant flowing into the first flow channel 141 from inlet 144 flows from the head end to the tail end. The refrigerant flowing through the first flow channel 141 flows from the tail end to the head end in the second flow channel 142 and finally exits from outlet 145. The flow direction of the refrigerant in the first flow channel 141 is opposite to that in the second flow channel 142. Furthermore, because the refrigerant gradually heats up during its flow due to heat absorption, the temperature of the refrigerant in the first flow channel 141 gradually increases from the head end to the tail end; that is, the cooling intensity of the refrigerant in the first flow channel 141 on the external liquid gradually decreases from the head end to the tail end. Conversely, the temperature of the refrigerant in the second flow channel 142 gradually increases from the tail end to the head end; that is, the cooling intensity of the refrigerant in the second flow channel 142 on the external liquid gradually decreases. The cooling intensity gradually decreases from the tail end to the head end. The cooling effect of the refrigerant in the first flow channel 141 on the external liquid and the cooling effect of the refrigerant in the second flow channel 142 on the external liquid can be superimposed to balance the difference in cooling effect at various points along the axial direction of the evaporator 100. This avoids the situation where the liquid at the head end of the evaporator 100 is prone to freezing or even deep freezing due to the large temperature difference between the two ends of the evaporator 100. This improves the effect of the evaporator 100 cooling liquid forming ice slush. It can also reduce the stirring resistance of the stirring rod 500, thereby reducing the drive load of the stirring device motor, ensuring the performance stability of the motor, and preventing the discharge nozzle 410 of the snow melting machine from being frozen and preventing the ice slush from being discharged.

[0046] In other embodiments, the first flow channel, the second flow channel, and the transition flow channel can also be constituted by a double helix tube disposed between the inner shell 110 and the outer shell 120. In this case, the double helix tube includes two single helix tubes wound together, wherein the inner cavity of one single helix tube constitutes the first flow channel, and the inner cavity of the other single helix tube constitutes the second flow channel. The inlet and outlet are respectively located at the head ends of the two helix tubes, and the tail ends of the two helix tubes are connected together and communicate with each other. The specific structure of the double helix tube can be referred to the double helix tube described in CN202430319U, or other prior art. The specific structure of the double helix tube will not be described in detail here.

[0047] In addition to the preferred embodiments described above, there are other embodiments of this utility model. Those skilled in the art can make various changes and modifications based on this utility model. As long as they do not depart from the spirit of this utility model, they should all fall within the scope defined in the claims of this utility model.

Claims

1. An evaporator for a snow melter, comprising an inner shell and an outer shell fitted outside the inner shell, a flow passage spirally extending from a head end to a tail end between the peripheries of the inner shell and the outer shell, the flow passage having an inlet for inflow of refrigerant and an outlet for outflow of refrigerant, characterized in that, The flow channel includes a first flow channel and a second flow channel arranged in a double-headed spiral shape. The inlet is located at the head end of the first flow channel, and the outlet is located at the head end of the second flow channel. The tail ends of the first flow channel and the tail ends of the second flow channel are connected. The refrigerant flowing in from the inlet flows through the first flow channel and the second flow channel in sequence and then flows out from the outlet.

2. An evaporator for a snow melter as defined in claim 1, characterized in that The cross-sectional area of ​​the first flow channel gradually increases from the head end to the tail end.

3. An evaporator for a snow melter as defined in claim 1, wherein The cross-sectional area of ​​the second flow channel gradually decreases from the tail end to the head end.

4. An evaporator for a snow melter as defined in claim 1, wherein The spiral length of the second flow channel is greater than that of the first flow channel, so that the head end of the second flow channel is offset from the head end of the first flow channel in the circumferential direction.

5. An evaporator for a snow melter as defined in claim 1, wherein The tail end of the first flow channel and the tail end of the second flow channel are smoothly connected by an arc-shaped transition flow channel.

6. An evaporator for a snow melter as defined in claim 1, wherein The evaporator also includes an intermediate sleeve disposed circumferentially between the inner shell and the outer shell. The intermediate sleeve is provided with a double-headed spiral groove with its head ends staggered and its tail ends connected. The outer circumferential surface of the inner shell, the inner circumferential surface of the outer shell, and the double-headed spiral groove cooperate to form a first flow channel and a second flow channel.

7. An evaporator for a snow melter as defined in claim 6, wherein The inner surface of the intermediate sleeve is bonded to the outer peripheral surface of the inner shell; and / or, the outer surface of the intermediate sleeve is bonded to the inner peripheral surface of the outer shell.

8. An evaporator for a snow melter as defined in claim 6, wherein The axial length of the inner shell is L1, the axial length of the intermediate sleeve is L2, and the axial inner length of the outer shell is L3, where L1 < L2 < L3.

9. An evaporator for a snow melter as defined in claim 1, wherein The outer casing is open at one end and closed at the other end. The inlet and the outlet are close to the closed end of the outer casing. The evaporator includes an inlet pipe communicating with the inlet and an outlet pipe communicating with the outlet. The inlet pipe and the outlet pipe are staggered circumferentially.

10. An evaporator for a snow melter as defined in claim 9, wherein Both the portion of the inlet tube and the portion of the outlet tube extend radially and have an included angle θ between them, where 15°≤θ≤180°.

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