Evaporator coil and refrigeration equipment

Abstract

The invention discloses an evaporator coil pipe and refrigeration equipment, and relates to the technical field of refrigeration, the refrigeration equipment comprises the evaporator coil pipe, the evaporator coil pipe comprises a liquid inlet pipe, a liquid outlet pipe and a liquid outlet pipe, and a plurality of first socket holes are formed in the pipe wall of the liquid inlet pipe; the number of the heat dissipation pipes is matched with that of the first socket holes, the first ends of the heat dissipation pipes are provided with the first socket holes in a one-to-one correspondence mode, and the heat dissipation pipes are installed in the corresponding first socket holes; a second socket hole corresponding to the first socket hole is formed in the pipe wall of the exhaust pipe, and the second end of the heat dissipation pipe is installed in the second socket hole; the cooling part is arranged in the exhaust pipe, a liquid inlet is formed in the cooling part, the cooling part comprises cooling pipes, the number of the cooling pipes is the same as that of the heat dissipation pipes, the cooling pipes correspond to the heat dissipation pipes one to one, and annular channels are formed between the cooling pipes and the heat dissipation pipes. According to the invention, the cooling part is arranged to cool and absorb heat in a vapor refrigerant conveying area of the evaporator coil, and a double-layer sleeve type structure is adopted, so that the refrigeration efficiency is greatly improved.

Description

Technical Field

[0001] This invention relates to the field of refrigeration, and particularly to an evaporator coil and a refrigeration device. Background Technology

[0002] The evaporator coil is a key component of a refrigeration system. It is typically made of bent and coiled metal tubes. The refrigerant flows inside the tubes, evaporating and vaporizing by absorbing heat from the outside. Thanks to its large surface area, it effectively exchanges heat with the surrounding air, thus achieving a cooling effect and playing a vital role in refrigeration.

[0003] Evaporator coils typically use refrigerant to absorb heat for cooling. Due to the technical limitations of refrigerant heat absorption cooling, half the length of the evaporator coil is usually filled with refrigerant, while the other half is used to transport the vaporized refrigerant after heat absorption. This results in poor cooling performance of the evaporator coil that transports the vaporized refrigerant, which in turn affects the cooling performance of the entire refrigeration system. Summary of the Invention

[0004] The purpose of this invention is to solve the problem of poor cooling performance of existing evaporator coils, which affects the overall cooling effect of the refrigeration system. This invention provides an evaporator coil and refrigeration equipment. By incorporating a cooling section, the other half of the evaporator coil, which transports gaseous refrigerant, is cooled and absorbs heat without affecting the original evaporation heat absorption within the evaporator coil. A double-layered sleeve structure is used to ensure that the refrigerant's return flow is not affected by changes in gas pressure after evaporation. The gas circulates back through the exhaust pipe, and the refrigeration cycle is unaffected by pressure changes after evaporation, greatly improving cooling efficiency.

[0005] To solve the above-mentioned technical problems, embodiments of the present invention disclose an evaporator coil, comprising: The liquid inlet pipe extends horizontally to accommodate refrigerant. Multiple first socket holes are provided on the pipe wall in the horizontal direction, and the first socket holes are evenly spaced. Multiple heat dissipation tubes are provided, the number of which matches the number of first socket holes. Each heat dissipation tube has a first socket hole at its first end. Each heat dissipation tube is vertically installed in its corresponding socket hole, and the heat dissipation tube is connected to the liquid inlet tube. The exhaust pipe extends horizontally and has multiple second sockets on its wall that correspond to the first socket. The second ends of the heat dissipation pipe are installed in the second sockets one by one and communicate with the exhaust pipe. The exhaust pipe also has an exhaust hole. The cooling section is located inside the exhaust pipe and has a liquid inlet. The cooling section includes multiple cooling tubes of the same number as the heat dissipation tubes. Each cooling tube corresponds to one heat dissipation tube. The cooling tubes are installed inside the heat dissipation tubes and are located above the heat dissipation tubes. There is a gap between the cooling tubes and the heat dissipation tubes so that an annular channel is formed between the cooling tubes and the heat dissipation tubes. The refrigerant flows into the heat dissipation pipe through the liquid inlet pipe, absorbs heat and evaporates in the heat dissipation pipe to form a vaporized refrigerant, and the vaporized refrigerant flows vertically upward into the exhaust pipe and is discharged through the exhaust hole. The refrigerant flows into the cooling pipe through the liquid inlet. The cooling pipe is used to cool the vaporized refrigerant above the heat dissipation pipe after it has absorbed heat.

[0006] By adopting the above technical solution, a cooling section is provided to cool and absorb heat in the other half of the evaporator coil, which transports vaporized refrigerant, without affecting the original evaporation heat absorption in the evaporator coil. The double-layer sleeve structure ensures that the refrigerant return process is not affected by the gas pressure change after evaporation. The gas circulates back from the exhaust pipe and is not affected by the pressure change after evaporation, so the refrigeration cycle is not affected, which greatly improves the refrigeration efficiency.

[0007] According to another specific embodiment of the present invention, the cooling part further includes an infusion tube, the infusion tube wall is provided with a third socket hole, the infusion tube extends into the exhaust pipe and is sealed to both ends of the exhaust pipe, along the extension direction of the infusion tube, the infusion tube is provided with a plurality of third socket holes corresponding to the cooling tube, the number of third socket holes corresponds to the number of cooling tubes, and the infusion tube is also provided with an air outlet hole. The cooling tube is installed inside the heat dissipation tube, and the first end of the cooling tube is installed in the third socket. The inlet is located on the infusion pipe. The refrigerant flows into the infusion pipe through the inlet and then into the cooling pipe. After absorbing heat and evaporating, the refrigerant in the cooling pipe is discharged through the vent hole into the exhaust pipe and then discharged through the exhaust hole.

[0008] According to another specific embodiment of the present invention, the embodiment of the present invention discloses that a first support pad is provided on the outer side wall of the infusion tube, and the first support pad fixes the infusion tube inside the venting pipe; The first support pad has multiple micro-holes penetrating both ends.

[0009] According to another specific embodiment of the present invention, a second support pad is provided on the outer wall of the cooling tube, and the second support pad fixes the cooling tube inside the heat dissipation tube. The second support pad has multiple second micro-holes penetrating both ends.

[0010] According to another specific embodiment of the present invention, the embodiment of the present invention discloses a cooling tube with a length of 33%-50% of the total length of a heat dissipation tube.

[0011] According to another specific embodiment of the present invention, the embodiment of the present invention discloses that the cooling pipe has an opening at the bottom in the vertical direction, and the refrigerant flows into the cooling pipe and then falls into the heat dissipation pipe.

[0012] The present invention also discloses a refrigeration device, including a refrigerant delivery device and an evaporator coil as described in any of the above specifications, wherein the refrigerant delivery device is used to deliver refrigerant to the liquid inlet pipe and the cooling section.

[0013] According to another specific embodiment of the present invention, the refrigerant conveying device includes a liquid receiver, a gas-liquid separator, and a compressor, wherein: The receiver is used to store refrigerant. The height of the receiver is higher than that of the evaporator coil to deliver refrigerant to the inlet pipe and the cooling section. The gas-liquid separator is connected to the exhaust pipe, receives the gaseous refrigerant from the exhaust pipe, and separates the gaseous refrigerant into gas and liquid. The gas-liquid separator is also connected to the compressor and the receiver respectively, and is used to send the gaseous refrigerant into the compressor and the liquid refrigerant into the receiver. The compressor is also connected to a liquid receiver to compress the gaseous refrigerant into a liquid state and then deliver it to the liquid receiver.

[0014] According to another specific embodiment of the present invention, the refrigerant conveying device further includes a refrigerant pump, which is connected to a liquid receiver, an inlet pipe and a cooling section, respectively, for conveying the refrigerant in the liquid receiver to the inlet pipe and the cooling section.

[0015] According to another specific embodiment of the present invention, the calculation formulas for the flow rate of refrigerant pumped to the inlet pipe and the cooling section are disclosed as follows:

[0016] Where Q is the refrigerant flow rate. For cooling capacity, Cooling capacity per unit mass The density of the liquid refrigerant; The formula for calculating the head of the refrigerant pump when delivering refrigerant to the inlet pipe and cooling section is:

[0017] in, For evaporator flow resistance pressure drop, This refers to the pressure drop along the pipeline plus local resistance. For pressure drop of valves and accessories, Liquid refrigerant density acceleration due to gravity This is the geometric height difference; The formula for calculation is:

[0018] in, Darcy's coefficient of friction For fluid density, For fluid velocity, This represents the local drag coefficient.

[0019] The beneficial effects of this application are as follows: It provides an evaporator coil and a refrigeration device. By setting a cooling section, the other half of the area in the evaporator coil that transports gaseous refrigerant is cooled and heat absorbed without affecting the original evaporation heat absorption in the evaporator coil. The double-layer sleeve structure ensures that the refrigerant return process is not affected by the gas pressure change after evaporation. The gas circulates back from the exhaust pipe and is not affected by the pressure change after evaporation. The refrigeration cycle is not affected, which greatly improves the refrigeration efficiency. Attached Figure Description

[0020] Figure 1 This diagram illustrates the structure of the evaporator coil according to an embodiment of the present invention. Figure 2 This diagram shows the structure of the exhaust pipe of the evaporator coil according to an embodiment of the present invention; Figure 3 This diagram shows the structure of the first support pad of the evaporator coil according to an embodiment of the present invention; Figure 4 A schematic diagram of the structure of the second support pad of the evaporator coil in an embodiment of the present invention is shown. Detailed Implementation

[0021] The following specific embodiments illustrate the implementation of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification. Although the description of the present invention is presented in conjunction with preferred embodiments, this does not mean that the features of the invention are limited to these embodiments. On the contrary, the purpose of describing the invention in conjunction with embodiments is to cover other options or modifications that may be derived based on the claims of the present invention. To provide a deep understanding of the invention, many specific details will be included in the following description. The invention may also be implemented without using these details. Furthermore, to avoid confusion or obscuring the focus of the invention, some specific details will be omitted in the description. It should be noted that, unless otherwise specified, the embodiments and features in the embodiments of the present invention can be combined with each other.

[0022] It should be noted that in this specification, similar reference numerals and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.

[0023] In the description of this embodiment, it should be noted that the terms "upper", "lower", "inner", "bottom", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, or the orientation or positional relationship that the product of the invention is usually placed in during use. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limiting the present invention.

[0024] The terms “first”, “second”, etc., are used only to distinguish descriptions and should not be interpreted as indicating or implying relative importance.

[0025] In the description of this embodiment, it should also be noted that, unless otherwise explicitly specified and limited, the terms "set up," "connected," and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this embodiment based on the specific circumstances.

[0026] To make the objectives, technical solutions, and advantages of the present invention clearer, the embodiments of the present invention will be described in further detail below with reference to the accompanying drawings.

[0027] Reference Figures 1 to 4This application provides an evaporator coil, comprising: a liquid inlet pipe 1, extending horizontally to accommodate refrigerant, wherein a plurality of first socket holes 11 are provided on the wall of the liquid inlet pipe 1 in the horizontal direction, and the first socket holes 11 are equally spaced; a plurality of heat dissipation pipes 2, the number of which matches the number of the first socket holes 11, each heat dissipation pipe 2 having a first socket hole 11 corresponding to its first end, and each heat dissipation pipe 2 being vertically installed in its corresponding first socket hole 11 and communicating with the liquid inlet pipe 1; and an exhaust pipe 3, extending horizontally, wherein a plurality of second socket holes 32 corresponding to the first socket holes 11 are provided on the wall of the exhaust pipe 3, and the second ends of the heat dissipation pipes 2 are respectively installed in the second socket holes 32 and communicating with the liquid inlet pipe 1. The exhaust pipe 3 is connected and also has an exhaust hole 31. The cooling section 4 is set inside the exhaust pipe 3 and has a liquid inlet. The cooling section 4 includes a plurality of cooling pipes 41 with the same number as the heat dissipation pipes 2. Each cooling pipe 41 corresponds to one heat dissipation pipe 2. The cooling pipe 41 is installed inside the heat dissipation pipe 2 and is located above the heat dissipation pipe 2. There is a gap between the cooling pipe 41 and the heat dissipation pipe 2 so that an annular channel is formed between the cooling pipe 41 and the heat dissipation pipe 2. The refrigerant flows into the heat dissipation pipe 2 through the liquid inlet pipe 1. After absorbing heat and evaporating in the heat dissipation pipe 2, it forms a vapor refrigerant. The vapor refrigerant flows vertically upward into the exhaust pipe 3 and is discharged through the exhaust hole 31. The refrigerant flows into the cooling pipe 41 through the liquid inlet. The cooling pipe 41 is used to cool the vapor refrigerant above the heat dissipation pipe 2 after absorbing heat.

[0028] In this embodiment, the inlet pipe 1 is made of metal, with sealing structures at both ends to prevent abnormal leakage of refrigerant from both ends. This ensures that the refrigerant can only flow into the corresponding heat dissipation pipe 2 through the first socket 11. The edges of the first socket 11 are chamfered to facilitate smoother insertion of the heat dissipation pipe 2, avoid scratching the surface of the heat dissipation pipe 2, and ensure the sealing and structural integrity of the connection. The first sockets 11 are evenly spaced to ensure that the refrigerant can be evenly distributed into each heat dissipation pipe 2.

[0029] The heat sink 2 is made of a metal material with good thermal conductivity, such as copper. Its outer surface is designed with a heat dissipation fin structure to increase the heat dissipation area and improve heat dissipation efficiency. When the first end of the heat sink 2 is inserted into the first socket 11 of the liquid inlet pipe 1, it is sealed by welding to prevent refrigerant leakage at the connection and ensure a smooth transition of refrigerant from the liquid inlet pipe 1 to the heat sink 2. Similarly, when the second end of the heat sink 2 is inserted into the second socket 32 ​​of the exhaust pipe 3, the same sealing method is used to allow the vaporized refrigerant to flow smoothly from the heat sink 2 into the exhaust pipe 3.

[0030] The horizontal extension length of the exhaust pipe 3 is adapted to that of the liquid inlet pipe 1. The exhaust port 31 is opened at a high position on the top or side of the exhaust pipe 3, so that the gaseous refrigerant can be smoothly discharged by its own upward flow trend.

[0031] The inner wall of the exhaust pipe 3 is smoothed to reduce the resistance when the gaseous refrigerant flows, so that the gaseous refrigerant can quickly and smoothly converge and be discharged from the exhaust port 31.

[0032] One end of the exhaust pipe 3 has an opening. A portion of the cooling section 4 extends upwards from the opening, and an inlet is located at the upward-facing portion of the cooling section 4. The inlet is connected to an external refrigerant supply source. Each cooling pipe 41 is installed above the heat dissipation pipe 2, and the outer diameter of each cooling pipe 41 is smaller than the inner diameter of the heat dissipation pipe 2, creating a gap between the cooling pipe 41 and the heat dissipation pipe 2. A ring-shaped channel is formed between the cooling pipe 41 and the heat dissipation pipe 2, through which the vaporized refrigerant flows vertically upwards and into the exhaust pipe 3 above. The ring-shaped channel ensures that the normal flow of the vaporized refrigerant within the heat dissipation pipe 2 is not affected. The cooling pipe 41 has a thin-walled design to enhance heat transfer efficiency, allowing the refrigerant inside the pipe to quickly absorb the heat from the vaporized refrigerant within the heat dissipation pipe 2.

[0033] After the refrigerant enters the inlet pipe 1 from the external liquid supply system, it is evenly distributed into each heat dissipation pipe 2 by its own pressure and the reasonable layout of each first socket 11. After entering the heat dissipation pipe 2, the refrigerant exchanges heat with the air or other media that need to dissipate heat outside the heat dissipation pipe 2. The refrigerant continuously absorbs heat and gradually evaporates from a liquid state to a vapor state. The vaporized refrigerant flows upward along the heat dissipation pipe 2 and finally flows into the exhaust pipe 3.

[0034] When the vaporized refrigerant enters the exhaust pipe 3, refrigerant flows into the cooling pipe 41 above. Through heat transfer between the cooling pipe 41 wall and the vaporized refrigerant, the vaporized refrigerant, after absorbing heat, is cooled down. The cooled vaporized refrigerant continues to flow towards the exhaust port 31 and is finally discharged into the subsequent refrigeration cycle system through the exhaust port 31. This completes the process of heat absorption, evaporation, cooling and discharge of the refrigerant in the evaporator coil, ensuring the efficient and stable operation of the entire refrigeration system.

[0035] By adopting the above technical solution, and by setting up a cooling section 4, the other half of the area in the evaporator coil that transports vaporized refrigerant is cooled and heat absorbed without affecting the original evaporation heat absorption in the evaporator coil. The double-layer sleeve structure ensures that the refrigerant return process is not affected by the gas pressure change after evaporation. The gas circulates back from the exhaust pipe 3 and is not affected by the pressure change after evaporation. The refrigeration cycle is not affected, which greatly improves the refrigeration efficiency.

[0036] In one feasible embodiment, the cooling section 4 further includes an infusion tube 42, the wall of which is provided with a third socket hole. The infusion tube 42 extends into the exhaust pipe 3 and is sealed to both ends of the exhaust pipe 3. Along the extension direction of the infusion tube 42, a plurality of third socket holes are provided at the location corresponding to the cooling tube 41. The number of third socket holes corresponds to the number of cooling tubes 41. An air outlet is also provided on the infusion tube 42. Cooling tube 41 is installed inside heat dissipation tube 2, and the first end of cooling tube 41 is installed in the third socket hole; The inlet is located on the infusion pipe 42. The refrigerant flows into the infusion pipe 42 through the inlet and then into the cooling pipe 41. After absorbing heat and evaporating, the refrigerant in the cooling pipe 41 is discharged through the vent hole into the exhaust pipe 3 and then discharged through the exhaust hole 31.

[0037] In this embodiment, the infusion tube 42 extends upward from the opening of the exhaust pipe 3, the inlet is opened on the infusion tube 42, the part of the infusion tube 42 that extends into the exhaust pipe 3 is sealed and connected to both ends of the exhaust pipe 3, and the third socket hole opened on the tube wall of the infusion tube 42 has a diameter that matches the size of the cooling tube 41.

[0038] The vent on the infusion tube 42 allows the refrigerant, after absorbing heat and evaporating, to be discharged into the exhaust pipe 3 without causing abnormal pressure fluctuations within the exhaust pipe 3. The periphery of the vent is chamfered to avoid stress concentration points and prevent cracking due to long-term use.

[0039] The cooling pipe 41 is installed at the top of the heat dissipation pipe 2. No matter what kind of vibration or external force it is subjected to during equipment operation, it can always maintain a good heat transfer state and effectively cool the gaseous refrigerant in the heat dissipation pipe 2.

[0040] After the refrigerant flows into the inlet pipe 42, it enters each cooling pipe 41 through the third socket of the inlet pipe 42. The flow rate of the refrigerant into the cooling pipe 41 is controlled so that it just flows in without completely covering the upper end of the cooling pipe 41, preventing the refrigerant from being unable to flow into the cooling pipe 41. Inside the cooling pipe 41, the refrigerant also absorbs heat from the vaporized refrigerant in the heat dissipation pipe 2, and then evaporates. The evaporated refrigerant is discharged into the exhaust pipe 3 through the vent on the inlet pipe 42, where it mixes with the original vaporized refrigerant in the exhaust pipe 3, and finally discharged into the subsequent refrigeration cycle system through the exhaust port 31 of the exhaust pipe 3. Throughout the exhaust pipe 3, the evaporated refrigerant in the cooling pipe 41 continuously exchanges heat with the rising vaporized refrigerant in the heat dissipation pipe 2, ensuring that the temperature of the discharged refrigerant is within a suitable range, thus guaranteeing the efficient and stable operation of the entire refrigeration system.

[0041] In one feasible embodiment, a first support pad 5 is fitted on the outer wall of the infusion tube 42, and the first support pad 5 fixes the infusion tube 42 inside the exhaust pipe 3. The first support pad 5 has multiple first microholes 51 extending through both ends of it.

[0042] A second support pad 6 is fitted on the outer wall of the cooling tube 41, and the second support pad 6 fixes the cooling tube 41 inside the heat dissipation tube 2. The second support pad 6 has multiple second microholes 61 that penetrate both ends of it.

[0043] In this embodiment, the first support pad 5 is made of a material that is elastic, heat-resistant, and has good chemical stability. It is made of fluororubber, and the first micropore 51 is designed to be circular, ensuring uniform ventilation and heat exchange while avoiding stress concentration points. The pore size of the first micropore 51 is in the range of 0.1-1 mm, allowing the gaseous refrigerant in the exhaust pipe 3 to pass smoothly through the first micropore 51 and exchange heat with the infusion pipe 42 and the surrounding area of ​​the cooling pipe 41, while also maintaining the structural stability of the first support pad 5 and reliably fixing the infusion pipe 42. In the axial direction of the first support pad 5, 5-10 first micropores 51 are evenly distributed per centimeter, and in the circumferential direction, they are distributed at equal angular intervals, ensuring balanced heat transfer of the refrigerant in all directions and improving the working efficiency of the entire cooling section 4 within the exhaust pipe 3.

[0044] The inner surface of the first support pad 5 is tightly fitted to the outer wall of the infusion tube 42. The fit is achieved by an interference fit to prevent the first support pad 5 from sliding or shifting relative to the infusion tube 42 during equipment operation.

[0045] The second support pad 6 is also made of fluororubber. The pore size of the second micropore 61 is in the range of 0.05-0.5 mm. The smaller pore size helps to adjust the heat exchange efficiency between the refrigerant and the cooling tube 41, ensuring the second support pad 6 is firmly fixed to the cooling tube 41. In the axial direction of the second micropore 61, 8-12 second micropores 61 are evenly distributed per centimeter, and in the circumferential direction, they are also distributed at equal angles. This achieves uniform and sufficient heat exchange between the vapor refrigerant in the heat dissipation tube 2 and the refrigerant in the cooling tube 41 in all directions, maximizing the cooling effect of the cooling tube 41 and improving the overall cooling effect of the evaporator coil.

[0046] The inner surface of the second support pad 6 is tightly fitted to the outer wall of the heat dissipation pipe 2. The fit is achieved by an interference fit to prevent the second support pad 6 from sliding or shifting relative to the heat dissipation pipe 2 during equipment operation.

[0047] In one feasible embodiment, the length of a cooling tube 41 is 33%-50% of the total length of a heat sink 2.

[0048] In this embodiment, based on the evaporation characteristics and heat exchange efficiency of the refrigerant within the heat dissipation pipe 2, the length of the cooling pipe 41 is selected to be 33%-50% of the total length of the heat dissipation pipe 2, preferably 33%. When the refrigerant enters the heat dissipation pipe 2, it gradually absorbs heat and evaporates from the bottom. As it flows upwards, the proportion of vaporized refrigerant gradually increases, and the evaporation process is essentially completed by the time it reaches the upper part of the heat dissipation pipe 2. Controlling the length of the cooling pipe 41 within this range ensures that it precisely covers the area where the vaporized refrigerant is concentrated within the heat dissipation pipe 2, allowing for targeted cooling of the vaporized refrigerant that has completed its main evaporation process. This avoids excessive contact between the cooling pipe 41 and the liquid refrigerant at the bottom of the heat dissipation pipe 2 due to excessive length, thereby reducing unnecessary cooling loss.

[0049] Meanwhile, this length ratio ensures sufficient contact time and area between the cooling pipe 41 and the rising vaporous refrigerant inside the heat dissipation pipe 2. If the cooling pipe 41 is shorter than 33% of the length of the heat dissipation pipe 2, the cooling effect may be poor due to insufficient contact area, and the temperature of the vaporous refrigerant may not be effectively reduced. If it exceeds 50%, the lower end of the cooling pipe 41 will penetrate deep into the liquid refrigerant area inside the heat dissipation pipe 2, which will not only interfere with the normal heat absorption and evaporation process of the liquid refrigerant, but also cause a decrease in heat exchange efficiency due to the small temperature difference between the refrigerant inside the cooling pipe 41 and the liquid refrigerant, thus increasing energy consumption.

[0050] Furthermore, this length ratio design also ensures the compactness of the entire evaporator coil structure. While guaranteeing the cooling effect, it avoids increasing the complexity of the overall structure and material costs by making the cooling pipe 41 too long, while reserving reasonable space for the flow of refrigerant in the heat dissipation pipe 2, ensuring that the vaporized refrigerant can flow smoothly upward to the exhaust pipe 3, maintaining the efficient operation of the entire refrigerant circulation system.

[0051] In one feasible embodiment, the cooling pipe 41 has an opening at the bottom in the vertical direction. After the refrigerant flows into the cooling pipe 41, it falls into the heat dissipation pipe 2 through the cooling pipe 41.

[0052] In this embodiment, the bottom of the cooling pipe 41 has an opening to facilitate the smooth flow of refrigerant from the infusion pipe 42 into the cooling pipe 41. The diameter of the opening can be set between 2 and 5 mm. This avoids the refrigerant from falling too quickly from the cooling pipe 41 into the heat dissipation pipe 2 if the opening is too large, which would prevent the refrigerant in the cooling pipe 41 from fully exchanging heat with the vaporized refrigerant in the heat dissipation pipe 2 and thus affecting the cooling effect. If the opening is too small, the refrigerant will flow into the heat dissipation pipe 2 too slowly, and may even cause blockage, hindering the normal circulation of refrigerant in the entire evaporator coil.

[0053] The opening is located at the very center of the bottom of the cooling pipe 41, so that all parts inside the heat dissipation pipe 2 can receive the refrigerant from the cooling pipe 41 in a relatively even manner.

[0054] When the refrigerant flows from the inlet pipe 42 into the cooling pipe 41 through the third socket, it flows downwards along the pipe wall within the cooling pipe 41, continuously absorbing heat from the rising vaporized refrigerant in the heat dissipation pipe 2, thus achieving initial cooling. Upon reaching the bottom opening, the refrigerant falls into the heat dissipation pipe 2 under gravity, mixing with the existing refrigerant (including liquid and vaporized refrigerant) in the heat dissipation pipe 2. Since the refrigerant temperature in the cooling pipe 41 is relatively low, its mixing lowers the overall temperature of the refrigerant in the heat dissipation pipe 2, further improving the heat absorption efficiency of the heat dissipation pipe 2. This allows subsequent refrigerant to absorb heat and evaporate more quickly, enhancing the overall cooling effect of the evaporator coil.

[0055] Meanwhile, with an opening at the bottom of the cooling pipe 41, part of the refrigerant flowing into the cooling pipe 41 directly absorbs heat from the vaporized refrigerant in the heat dissipation pipe 2, and then evaporates. The evaporated refrigerant rises along the liquid delivery pipe 42 and is discharged into the exhaust pipe 3 through the vent, where it mixes with the original vaporized refrigerant in the exhaust pipe 3. The other part falls into the heat dissipation pipe 2 through the opening. Since the annular channel formed between the cooling pipe 41 and the heat dissipation pipe 2 allows the vaporized refrigerant to rise directly along the annular channel, the refrigerant in the cooling pipe 41 can fall directly into the heat dissipation pipe 2 through the opening without being affected by the gas pressure of the vaporized refrigerant. At the same time, the gas evaporated by the refrigerant in the cooling pipe 41 during its fall can also rise along the annular channel with the vaporized refrigerant and be discharged into the exhaust pipe 2.

[0056] Embodiments of the present invention also disclose a refrigeration device, including a refrigerant delivery device and an evaporator coil as described in any of the above specifications, wherein the refrigerant delivery device is used to deliver refrigerant to the liquid inlet pipe 1 and the cooling section 4. The refrigerant delivery device includes a liquid receiver, a gas-liquid separator, and a compressor, wherein: The receiver is used to store refrigerant. The height of the receiver is higher than that of the evaporator coil so as to supply refrigerant to the inlet pipe 1 and the cooling section 4. The gas-liquid separator is connected to the exhaust pipe 3, receives the gaseous refrigerant from the exhaust pipe 3, and performs gas-liquid separation on the gaseous refrigerant. The gas-liquid separator is also connected to the compressor and the liquid receiver respectively, and is used to send the gaseous refrigerant into the compressor and the liquid refrigerant into the liquid receiver. The compressor is also connected to a liquid receiver to compress the gaseous refrigerant into a liquid state and then deliver it to the liquid receiver.

[0057] The refrigerant delivery equipment also includes a refrigerant pump, which is connected to the liquid receiver, the inlet pipe and the cooling section, respectively, and is used to deliver the refrigerant in the liquid receiver to the inlet pipe and the cooling section.

[0058] In this embodiment, there are two ways in which the liquid receiver supplies refrigerant to the inlet pipe 1 and the cooling section 4. One way is that the height of the liquid receiver is higher than the evaporator coil, and the refrigerant flows to the inlet pipe 1 and the cooling section 4 by gravity. The liquid receiver is usually equipped with a one-way valve, which is used to control the flow rate of the refrigerant in the liquid receiver so that the liquid level of the refrigerant after flowing into the heat dissipation pipe 2 through the inlet pipe 1 is at half the height of the heat dissipation pipe 2.

[0059] In one feasible embodiment, the receiver is connected to the inlet of the refrigerant pump, and a one-way valve on the receiver prevents refrigerant backflow. Simultaneously, the receiver receives liquid refrigerant from the gas-liquid separator (via the return pipe) and high-pressure liquid refrigerant discharged from the compressor (via the condenser). These three components form a layered buffer space within the receiver: the bottom area stores the liquid refrigerant, and the top is reserved as a gas-liquid separation buffer zone to prevent liquid refrigerant from directly entering the return pipe or condenser inlet.

[0060] The refrigerant pump output is divided into two branches: the main branch connects to the evaporator coil inlet pipe 1 via a first flow control valve, supplying refrigerant for evaporation to the heat dissipation pipe 2; the secondary branch connects to the cooling section 4 via a second flow control valve via a liquid delivery pipe 42, supplying refrigerant for cooling to the cooling pipe 41. The two flow control valves can be independently adjusted, distributing refrigerant according to an 8:2 ratio between the main and secondary branches.

[0061] The gas-liquid separator employs a structure combining cyclone separation and gravity settling: gaseous refrigerant from exhaust pipe 3 enters the separator cylinder tangentially. Under centrifugal force, liquid or mist-like refrigerant is thrown against the cylinder wall and flows down the wall, collecting in the bottom liquid accumulation area; gaseous refrigerant enters the top outlet along the central riser pipe. The bottom liquid accumulation area is controlled by a liquid level sensor to open the drain valve. When the liquid reaches the preset level, the drain valve opens, sending the liquid refrigerant back to the receiver, preventing liquid refrigerant from entering the compressor.

[0062] The outlet of the gas-liquid separator is connected to the suction end of the compressor through a check valve to ensure unidirectional flow of gaseous refrigerant; the drain pipe of the liquid accumulation area is connected to the return port of the liquid receiver, and the pipe is equipped with a throttling orifice to reduce the speed at which liquid refrigerant flows into the liquid receiver and reduce disturbance to the refrigerant state in the liquid receiver.

[0063] After the compressor draws in the low-pressure gaseous refrigerant from the gas-liquid separator, it is mechanically compressed into a high-temperature, high-pressure gaseous refrigerant, which is then discharged into the condenser pipe. The condenser pipe can be water-cooled or air-cooled (depending on the equipment type), allowing the high-temperature, high-pressure gaseous refrigerant to release heat and condense into a high-pressure liquid refrigerant. Finally, after being depressurized by the expansion valve, it is sent to the receiver, completing the closed-loop circulation of the refrigerant.

[0064] A pressure sensor and a bypass valve are installed between the compressor and the receiver. When the pressure in the receiver is too high, the bypass valve opens and sends some of the incompletely condensed gaseous refrigerant directly back to the compressor suction end to avoid overpressure in the receiver. When the system pressure is too low, the compressor automatically reduces its operating frequency and the amount of refrigerant output to maintain stable system pressure.

[0065] The liquid refrigerant in the receiver is split by the refrigerant pump and enters the heat dissipation tube 2 and cooling tube 41 of the evaporator coil respectively. The refrigerant in the heat dissipation tube 2 absorbs heat and evaporates into a gaseous state, and enters the gas-liquid separator through the exhaust pipe 3. After the refrigerant in the cooling pipe 41 absorbs heat from the vaporized refrigerant, part of it evaporates into vapor and enters the exhaust pipe 3 through the vent hole of the liquid delivery pipe 42. The remaining liquid refrigerant falls into the heat dissipation pipe 2 through the bottom opening of the cooling pipe 41 and participates in the heat absorption and evaporation process.

[0066] The gaseous refrigerant separated by the gas-liquid separator is compressed and condensed by the compressor and then flows back to the liquid receiver, while the liquid refrigerant returns directly to the liquid receiver, forming a complete cycle.

[0067] In one feasible embodiment, the formulas for calculating the flow rates of refrigerant pumped to inlet pipe 1 and cooling section 4 are as follows:

[0068] Where Q is the refrigerant flow rate. For cooling capacity, Cooling capacity per unit mass This refers to the density of the liquid refrigerant.

[0069] In this embodiment, the cooling capacity The heat exchange requirements of the evaporator coil dictate that when the temperature of the cooled space rises, the evaporator coil needs to remove more heat. Real-time increase; the refrigerant pump increases based on demand flow mapping. Automatic output adjustment: utilizing unit mass cooling capacity Liquid refrigerant density It can quickly calculate the required refrigerant flow rate Q for inlet pipe 1 (to ensure evaporation) and cooling section 4 (to ensure cooling) without manual intervention, so that the refrigerant delivery matches the refrigeration load.

[0070] When the superheat of the vapor refrigerant in heat dissipation pipe 2 is high (temperature much higher than evaporation temperature), the cooling flow rate is automatically increased based on the formula calculation. This utilizes the "heat absorption and cooling" characteristic of the refrigerant in cooling pipe 41 to allow more refrigerant to flow through cooling pipe 41, absorbing heat from the vapor refrigerant and reducing its superheat, thus preventing the compressor from drawing in high-temperature refrigerant and affecting efficiency. If the superheat of the vapor refrigerant is low (close to evaporation temperature), the flow rate of cooling section 4 is reduced to prioritize the supply of evaporating refrigerant to inlet pipe 1, preventing excessive cooling and refrigerant waste.

[0071] The flow distribution of the liquid inlet pipe 1 is achieved through a multi-pipe flow equalization structure. After the refrigerant enters the liquid inlet pipe 1, the resistance balance design of the pipe wall openings ensures that each heat dissipation pipe 2 receives a uniform flow. Even if the resistance of a single heat dissipation pipe 2 changes due to frost or dirt blockage, the flow of the adjacent heat dissipation pipe 2 can be automatically compensated to ensure the overall evaporation efficiency. This allows the total flow calculated by the formula to be stably converted into effective cooling for each heat dissipation pipe 2.

[0072] The flow rate of the vaporized refrigerant discharged from the exhaust pipe 3 (determined by the evaporation of the liquid inlet pipe 1 and the heat absorption of the cooling pipe 41) is adapted to the separation capacity of the gas-liquid separator. When the flow rate increases, the separator uses the gradient expansion design of the internal space (such as segmented diameter expansion) to allow the vapor and liquid to separate smoothly, avoiding the accidental intake of liquid refrigerant by the compressor due to sudden changes in flow rate. When the flow rate decreases, the separator maintains the separation effect through a slow-flow structure (such as a built-in damping mesh) to ensure the quality of compressor intake.

[0073] Among them, cooling capacity This is achieved by the refrigerant absorbing heat, i.e. (m represents the mass of refrigerant flowing through the evaporator per unit time, in kg / s). Also, due to mass... (V represents the volumetric flow rate of the cooling medium per unit time, expressed in m³ / s) 3 \s), substituting into The volumetric flow rate was obtained by sorting. Multiply by 3600 to convert to hourly flow rate. ,Right now .

[0074] The formula for calculating the head of the refrigerant pump supplying refrigerant to inlet pipe 1 and cooling section 4 is as follows:

[0075] in, For evaporator flow resistance pressure drop, This refers to the pressure drop along the pipeline plus local resistance. For pressure drop of valves and accessories, Liquid refrigerant density acceleration due to gravity This is the geometric height difference; The formula for calculation is:

[0076] in, Darcy's coefficient of friction For fluid density, For fluid velocity, This represents the local drag coefficient.

[0077] In this embodiment, the refrigerant pump head needs to be matched with changes in system resistance in real time to form a "calculation-adjustment" closed loop: When the evaporator is frosted / clogged If the pressure drop increases, the refrigerant pump automatically identifies changes in pressure drop through a flow resistance feedback algorithm and dynamically increases the head to ensure stable refrigerant flow; if the pressure drop decreases (such as after defrosting), the head is reduced to avoid energy waste.

[0078] Pipeline friction resistance When the refrigerant flow rate and temperature change, the pump's built-in physical property correlation model automatically calls upon the real-time refrigerant density. Speed ​​v correction calculation ensures that the head always matches the actual resistance.

[0079] Evaporator flow resistance Determined by the coupling characteristics of heat pipe 2 and refrigerant: When the refrigerant evaporates inside the heat pipe 2, the change in the two-phase flow state (liquid state → vapor-liquid mixture → gas state) will change the flow resistance characteristics. The pump uses a two-phase flow adaptation algorithm to predict sudden changes in flow resistance (such as the change from "plug flow" to "circular flow") and adjusts the head in advance to avoid flow interruption. When multiple heat exchange tubes 2 experience uneven frost formation leading to differences in flow resistance, the pump's output head is adjusted through the branch pipe flow equalization structure (resistance balancing design within the inlet pipe 1) to allow the refrigerant to flow preferentially to the heat exchange tubes 2 with lower flow resistance. Then, the bypass compensates for the pipes with higher flow resistance, ensuring overall flow distribution and effectively converting the pump's head into cooling power for each heat exchange tube 2.

[0080] Valve and accessory pressure drop Adaptive compensation design is adopted: When valves such as solenoid valves and gate valves are activated (such as system start-up, shutdown, and mode switching), the pump uses time-coordinated control to quickly adjust the head to compensate for pressure drop at the moment of sudden change in valve resistance, thus avoiding flow fluctuations. During long-term operation, valve wear leads to increased resistance. The pump learns from historical data to identify resistance drift trends and gradually increases the head as a "pre-compensation" measure to ensure stable flow until the valve is maintained or replaced.

[0081] The effect of the height difference between the inlet pipe 1 and the evaporator on the head is achieved through a gravity-pressure conversion mechanism: When the liquid inlet pipe 1 is higher than the evaporator When positive, the pump utilizes gravitational potential energy to assist in delivery, automatically reducing the head output and minimizing energy consumption; if the inlet pipe 1 is lower than the evaporator... If the value is negative, the head is increased to compensate for the gravitational drag, ensuring the refrigerant flows "against the current".

[0082] When equipment is installed at an angle (such as a refrigeration unit installed at an angle), the pump's built-in attitude sensing algorithm automatically corrects the angle. To ensure the actual impact and avoid insufficient flow due to calculation errors caused by geometric height differences.

[0083] Darcy coefficient of friction In conjunction with the pump's pulsation suppression design: Turbulent pulsation inside the pipe The Reynolds number can affect refrigerant flow, potentially causing instability. The pump compensates for this by adjusting output pulsation (e.g., by adjusting impeller blade angle and frequency) to counteract the interference of pipeline turbulence on the flow rate. The calculated values ​​are closer to the actual resistance. When local resistance When the layout of pipe fittings (elbows, tees) changes, the pump automatically adapts to different resistance combinations through a pipeline topology recognition algorithm to ensure accurate head calculation.

[0084] While the present invention has been illustrated and described with reference to certain preferred embodiments, those skilled in the art should understand that the above description is a further detailed explanation of the invention in conjunction with specific embodiments, and should not be construed as limiting the specific implementation of the invention to these descriptions. Various changes in form and detail can be made by those skilled in the art, including several simple deductions or substitutions, without departing from the spirit and scope of the invention.

Claims

1. An evaporator coil, characterized in that, include: The liquid inlet pipe extends horizontally to accommodate refrigerant. Along the horizontal direction, the wall of the liquid inlet pipe has multiple first socket holes, which are evenly spaced. Multiple heat dissipation tubes are provided, the number of which matches the number of first socket holes. Each heat dissipation tube has a first socket hole at its first end. Each heat dissipation tube is vertically installed in its corresponding first socket hole, and the heat dissipation tube is connected to the liquid inlet tube. An exhaust pipe extends along the horizontal direction. The exhaust pipe has multiple second sockets on its wall that correspond to the first socket. The second ends of the heat dissipation pipe are installed in the second sockets one by one and communicate with the exhaust pipe. The exhaust pipe also has an exhaust hole. The cooling section is located inside the exhaust pipe and has a liquid inlet. The cooling section includes a plurality of cooling tubes, the same number as the heat dissipation tubes. Each cooling tube corresponds to one heat dissipation tube. The cooling tubes are installed inside the heat dissipation tubes and located above the heat dissipation tubes. There is a gap between the cooling tubes and the heat dissipation tubes so that an annular channel is formed between the cooling tubes and the heat dissipation tubes. The refrigerant flows into the heat dissipation pipe through the inlet pipe, absorbs heat and evaporates in the heat dissipation pipe to form a vapor refrigerant, and the vapor refrigerant flows upward along the vertical direction into the exhaust pipe and is discharged through the exhaust hole. The refrigerant flows into the cooling pipe through the inlet, and the cooling pipe is used to cool the vaporized refrigerant above the heat dissipation pipe after it has absorbed heat.

2. The evaporator coil as described in claim 1, characterized in that, The cooling section also includes an infusion tube, the wall of which is provided with a third socket hole. The infusion tube extends into the exhaust pipe and is sealed to both ends of the exhaust pipe. Along the extension direction of the infusion tube, the infusion tube is provided with a plurality of third socket holes corresponding to the cooling tube. The number of third socket holes corresponds to the number of cooling tubes. The infusion tube is also provided with an air outlet. The cooling tube is disposed inside the heat dissipation tube, and the first end of the cooling tube is installed in the third socket hole; The inlet is located on the infusion pipe. The refrigerant flows into the infusion pipe through the inlet and then into the cooling pipe. After absorbing heat and evaporating, the refrigerant in the cooling pipe is discharged through the vent hole into the exhaust pipe and then discharged through the exhaust hole.

3. The evaporator coil as described in claim 2, characterized in that, A first support pad is fitted on the outer wall of the infusion tube, and the first support pad fixes the infusion tube inside the exhaust pipe; The first support pad has multiple micro-holes penetrating both ends.

4. The evaporator coil as described in claim 2, characterized in that, A second support pad is fitted on the outer wall of the cooling tube, and the second support pad fixes the cooling tube inside the heat dissipation tube; The second support pad has multiple second micro-holes penetrating both ends.

5. The evaporator coil as described in claim 2, characterized in that, The length of one of the cooling tubes is 33%-50% of the total length of the heat dissipation tube.

6. The evaporator coil as described in claim 1, characterized in that, Along the vertical direction, the cooling pipe has an opening at the bottom, and the refrigerant flows into the cooling pipe and then falls into the heat dissipation pipe.

7. A refrigeration device, characterized in that, It includes a refrigerant delivery device and an evaporator coil as described in any one of claims 1-6, wherein the refrigerant delivery device is used to deliver the refrigerant to the liquid inlet pipe and the cooling section.

8. The refrigeration equipment as described in claim 7, characterized in that, The refrigerant delivery equipment includes a liquid receiver, a gas-liquid separator, and a compressor, wherein: The liquid receiver is used to store the refrigerant, and the height of the liquid receiver is higher than that of the evaporator coil, so as to deliver the refrigerant to the liquid inlet pipe and the cooling section; The gas-liquid separator is connected to the exhaust pipe, receives the gaseous refrigerant from the exhaust pipe, and performs gas-liquid separation on the gaseous refrigerant. The gas-liquid separator is also connected to the compressor and the liquid receiver respectively, for sending the gaseous refrigerant into the compressor and the liquid refrigerant into the liquid receiver. The compressor is also connected to the liquid receiver for compressing the gaseous refrigerant into a liquid state and then delivering it to the liquid receiver.

9. The refrigeration equipment as described in claim 8, characterized in that, The refrigerant delivery equipment also includes a refrigerant pump, which is connected to the liquid receiver, the liquid inlet pipe and the cooling section respectively, and is used to deliver the refrigerant in the liquid receiver to the liquid inlet pipe and the cooling section.

10. The refrigeration equipment as described in claim 8, characterized in that, The calculation formulas for the flow rate of the refrigerant pump delivering the refrigerant to the inlet pipe and the cooling section are as follows: Where Q is the refrigerant flow rate. For cooling capacity, Cooling capacity per unit mass The density of the liquid refrigerant; The formula for calculating the head of the refrigerant pump that delivers the refrigerant to the inlet pipe and the cooling section is as follows: in, For evaporator flow resistance pressure drop, This refers to the pressure drop along the pipeline plus local resistance. For pressure drop of valves and accessories, Liquid refrigerant density acceleration due to gravity This is the geometric height difference; The The formula for calculation is: in, Darcy's coefficient of friction For fluid density, For fluid velocity, This represents the local drag coefficient.

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