Fractional condenser and refrigeration device

Abstract

The utility model belongs to the technical field of refrigeration equipment, and particularly relates to a fractional condenser and a refrigeration device, the fractional condenser comprises an outer pipe and an inner pipe, a sealed central cavity is formed in the outer pipe, the outer pipe is further provided with an air inlet pipe, an air outlet pipe and a fractional condensation pipe which are communicated with the central cavity, and the fractional condensation pipe is located at the bottom of the outer pipe; the inner pipe comprises a spiral pipe and straight pipe sections which are integrally formed, and the two straight pipe sections are arranged at the two axial ends of the spiral pipe respectively; wherein the spiral pipe is arranged in the central cavity, and the two straight pipe sections penetrate out of the two axial ends of the outer pipe. The fractional condenser provided by the utility model is simple in structure, and fewer in assembly welding spots, so that not only is the manufacturing process of the fractional condenser simple, but also welding slag and oxide skin generated in the welding process are fewer, the fractional condenser cannot be blocked, and the manufacturing yield of the fractional condenser is further ensured.

Description

Technical Field

[0001] This utility model belongs to the field of refrigeration equipment technology, and specifically relates to a condenser and a refrigeration device. Background Technology

[0002] Condensers are widely used in industries such as chemical, petroleum, solvent, pharmaceutical, food, light industry, textile, metallurgy, steel rolling, and coking. Related technologies typically employ multiple parallel inner tubes within the condenser to increase the heat exchange area, thereby improving the condenser's heat exchange efficiency. Complex structural designs are also used to connect these multiple inner tubes in parallel within the same passageway. This design results in numerous internal pipes and weld points, complicating manufacturing. Furthermore, weld slag and oxide scale generated during welding can easily accumulate inside the condenser, causing blockages and further increasing manufacturing defects.

[0003] Therefore, in view of the above shortcomings, this utility model is proposed. Utility Model Content

[0004] The purpose of this invention is to provide a condenser and a refrigeration device to solve the problem that the condenser in the prior art is prone to system clogging due to its complex process and numerous welding points.

[0005] The first aspect of this utility model provides a condenser, comprising:

[0006] An outer tube has a sealed central cavity inside. The outer tube is also provided with an air inlet pipe, an air outlet pipe, and a condensate distribution pipe that communicate with the central cavity. The condensate distribution pipe is located at the bottom of the outer tube.

[0007] The inner tube comprises an integrally formed spiral tube and two straight tube sections, which are respectively located at both ends of the spiral tube along its axial direction.

[0008] The spiral tube is disposed in the central cavity, and the two straight tube sections extend from the two axial ends of the outer tube.

[0009] The condenser provided by this utility model may also have the following additional technical features:

[0010] In one specific embodiment of this utility model, the outer tube includes a shell tube and a tapered portion connected to both ends of the shell tube, wherein the shell tube and the tapered portion are an integral structure.

[0011] In one specific embodiment of this utility model, the cone portion is a spin-formed structure.

[0012] In one specific embodiment of this utility model, the length of the spiral tube is not less than the length of the shell tube; and / or the ratio of the outer diameter of the spiral tube to the inner diameter of the outer tube is not less than 0.5.

[0013] In one specific embodiment of this utility model, the diameter of the outer tube is between 15mm and 100mm; and / or, the diameter of the straight tube section is between 3mm and 9.52mm.

[0014] In one specific embodiment of this utility model, the diameter of the spiral tube is at least 5 times the diameter of the straight tube section.

[0015] In one specific embodiment of this utility model, the inner tube is made of a smooth tube, or the inner tube is made of an internally threaded tube.

[0016] In one specific embodiment of this utility model, the outer tube is made of copper.

[0017] In one specific embodiment of this utility model, a heat preservation mechanism is further included, which is at least circumferentially disposed around the upper part of the outer tube.

[0018] The second aspect of this utility model also provides a refrigeration device, including the condenser described in any one of the above claims.

[0019] The condenser provided by this utility model includes an inner tube consisting of an integrally formed spiral tube and straight pipe sections. This design increases the length of the refrigerant flow path and the heat exchange area through the spiral tube, thereby improving heat exchange efficiency. Furthermore, the inner tube structure is simple and has no weld points, preventing the generation of weld slag and oxide scale that could clog it. During condenser assembly, only five weld points are required on the outer tube: the inlet pipe weld point, the outlet pipe weld point, the condenser tube weld point, and the weld points for the two straight pipe sections. This simplifies the manufacturing process and reduces the amount of weld slag and oxide scale generated during welding, preventing clogging and ensuring a high yield rate for the condenser. Attached Figure Description

[0020] To more clearly illustrate the specific embodiments of this utility model or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0021] Figure 1 This is a cross-sectional structural diagram of the condenser in one embodiment of the present invention.

[0022] Explanation of reference numerals in the attached figures:

[0023] 100-Friction condenser;

[0024] 10-Outer tube, 11-Shell tube, 12-Conical section; 20-Inner tube, 21-Helical tube, 22-Straight section;

[0025] 30 - Inlet pipe, 40 - Outlet pipe, 50 - Condensation pipe. Detailed Implementation

[0026] Exemplary embodiments of the present invention will now be described in more detail with reference to the accompanying drawings. While exemplary embodiments of the present invention are shown in the drawings, it should be understood that the present invention may be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this invention will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art.

[0027] It should be understood that the terminology used herein is for the purpose of describing particular exemplary embodiments only and is not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms “a,” “an,” and “described” as used herein may also include the plural forms. The terms “comprising,” “including,” “containing,” and “having” are inclusive and therefore indicate the presence of the stated features, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, elements, components, and / or combinations thereof. The method steps, processes, and operations described herein are not construed as requiring them to be performed in a particular order described or illustrated unless the order of performance is explicitly indicated. It should also be understood that additional or alternative steps may be used.

[0028] Although terms such as first, second, third, etc., may be used in this document to describe multiple elements, components, regions, layers, and / or segments, these elements, components, regions, layers, and / or segments should not be limited by these terms. These terms may be used only to distinguish one element, component, region, layer, or segment from another. Unless the context clearly indicates otherwise, terms such as "first," "second," and other numerical terms used herein do not imply order or sequence. Therefore, the first element, component, region, layer, or segment discussed below may be referred to as the second element, component, region, layer, or segment without departing from the teachings of the exemplary embodiments.

[0029] For ease of description, spatial relative terms may be used in the text to describe the relationship of one element or feature relative to another element or feature, as shown in the figure. These relative terms include, for example, "inside," "outside," "middle," "outer," "below," "below," "above," "over," etc. Such spatial relative terms are intended to include different orientations of the device in use or operation, other than those depicted in the figure. For example, if the device in the figure is flipped, an element described as "below other elements or features" or "below other elements or features" would subsequently be oriented as "above other elements or features" or "above other elements or features." Therefore, the example term "below" can include both upper and lower orientations. The device may be otherwise oriented (rotated 90 degrees or in other directions), and the spatial relative descriptors used in the text will be interpreted accordingly.

[0030] Most condensers on the market today have problems with complex manufacturing processes and numerous weld points. Due to the large number of weld points, the oxide scale and welding slag generated during the welding process can easily cause dirt and blockage in the condenser, thus affecting its function.

[0031] To address this technical problem, this utility model provides a condenser 100 with a relatively simple structure and fewer weld points, which can reduce the oxide scale and welding slag generated during the welding process, reduce the clogging of the condenser 100, and thus improve the heat exchange capacity of the condenser 100 and increase its economic value.

[0032] Reference Figure 1 The condenser 100 provided in this embodiment of the present invention includes an outer tube 10 and an inner tube 20. A sealed central cavity is formed inside the outer tube 10. The outer tube 10 is also provided with an air inlet pipe 30, an air outlet pipe 40 and a condenser pipe 50 communicating with the central cavity. The condenser pipe 50 is located at the bottom of the outer tube 10. The inner tube 20 includes an integrally formed spiral tube 21 and two straight pipe sections 22, which are respectively located at the two axial ends of the spiral tube 21. The spiral tube 21 is located in the central cavity, and the two straight pipe sections 22 extend out from the two axial ends of the outer tube 10.

[0033] Specifically, the outer pipe 10, together with the inlet pipe 30 and the outlet pipe 40, forms a first passage for the gas to be condensed to flow. The spiral tube 21 section of the inner pipe 20 is set inside the outer pipe 10, and the straight pipe sections 22 at both ends protrude out, forming a second passage for the refrigerant to flow. The gas to be condensed that enters the outer pipe 10 from the inlet pipe 30 exchanges heat with the refrigerant in the inner pipe 20. Part of it condenses into liquid and flows out from the condenser pipe 50, and part of it is discharged through the outlet pipe 40. In this way, the condensation function of the condenser 100 is realized.

[0034] Furthermore, in the aforementioned condenser 100, the inner tube 20 includes an integrally formed spiral tube 21 and straight tube sections 22. This increases the length of the refrigerant flow path and the heat exchange area through the spiral tube 21, thereby improving heat exchange efficiency. Additionally, the inner tube 20 has a simple structure and no weld points, preventing the generation of weld slag and oxide scale that could clog it. During the assembly of the condenser 100, only five weld points are required on the outer tube 10: the inlet pipe 30, the outlet pipe 40, the condenser tube 50, and the two straight tube sections 22. This simplifies the process and minimizes the amount of weld slag and oxide scale generated during welding, preventing clogging of the condenser 100 and ensuring a high yield rate for the condenser 100.

[0035] Furthermore, in order to reduce the formation of oxide scale on the surfaces of the inner tube 20 and outer tube 10 during the welding process, welding shielding gas can be connected to the inlet pipe 30, outlet pipe 40, and inner tube 20.

[0036] Furthermore, the height of the inlet pipe 30 should be higher than the liquid level in the condenser 100 to prevent the gas entering the outer pipe 10 through the inlet pipe 30 from making bubbles in the liquid.

[0037] In one embodiment, the outer tube 10 includes a shell tube 11 and a tapered portion 12 connected to both ends of the shell tube 11, wherein the shell tube 11 and the tapered portion 12 are integral structures.

[0038] Specifically, along the length of the outer tube 10, the shell tube 11 has a consistent cross-sectional profile and is specifically designed to accommodate the spiral tube 21 section of the inner tube 20. A tapered tube connects to both ends of the shell tube 11, and its cross-sectional dimensions decrease from the connection point with the shell tube 11 to the end, thus forming a smaller constriction at the end, which allows for a suitable connection with the straight tube section 22 of the inner tube 20. Furthermore, by making the shell tube 11 and the tapered section 12 an integral structure, welding on the outer tube 10 can be further reduced, thereby reducing the generation of weld slag and oxide scale, thus preventing blockage within the condenser 100 and improving the manufacturing yield of the condenser 100.

[0039] It should be noted that the cross-section of the shell tube 11 can be circular, square, or other varied shapes. Correspondingly, the cone 12 can be a cone, a square pyramid, or other pyramidal structures, which are not limited here.

[0040] In one embodiment, the cone 12 is a spin-formed structure.

[0041] Specifically, the outer tube 10 is made of a circular tube with a circular cross-section. The tapered portion 12 of the outer tube 10 is a conical structure formed by spinning and compressing the two ends of the circular tube. The shell tube 11 is the portion between the two tapered tubes. Spin forming refers to a process method that locally rotates and compresses the circular tube radially to reduce its diameter. During the diameter reduction, the pre-formed circular tube is placed in a clamping device and rotates with the rotation of the main shaft. The rotating wheel makes radial feed motion outside the circular tube. After one or more gradual deformations, a tapered portion 12 with a tapered constriction shape is obtained. Furthermore, the spin forming in this embodiment is carried out in a high-temperature environment.

[0042] In this embodiment, the tapered part 12 is made by spin forming process, so that the outer tube 10 can be assembled with the inner tube 20 which is thick in the middle and thin at both ends on the basis of integral forming of the outer tube 10, thereby realizing the integral forming of the outer tube 10.

[0043] Of course, it should be noted that the cone 12 can also be made using other thermoforming processes.

[0044] In one embodiment, the length of the spiral tube 21 is not less than the length of the shell tube 11.

[0045] Specifically, along its length, the shell tube 11 has a generally consistent radial dimension, while the dimension of the tapered portion 12 decreases sequentially from its end at the transition connection with the shell tube 11 until it is approximately the same as the diameter of the straight section 22 of the inner tube 20. The axial length of the spiral tube 21 directly affects the heat exchange area of ​​the inner tube 20; the longer the axial length of the spiral tube 21, the larger its heat exchange area. The spiral tube 21 is placed inside the outer tube 10, and since its length is not less than the length of the shell tube 11, most of its structure is located inside the shell tube 11, thus filling the shell tube 11 to achieve sufficient heat exchange and thereby improving the heat exchange efficiency of the condenser 100.

[0046] In one embodiment, the ratio of the outer diameter of the spiral tube 21 to the inner diameter of the outer tube 10 is not less than 0.5. Specifically, the ratio of the outer diameter of the spiral tube 21 to the inner diameter of the outer tube 10 can be 0.5, 0.6, 0.7, 0.8, 0.9, etc., and can be designed according to the required heat exchange. Preferably, the ratio of the outer diameter of the spiral tube 21 to the inner diameter of the outer tube 10 is 0.7-0.8.

[0047] It should be noted that the outer diameter of the spiral tube 21 directly affects the circumference of each spiral turn. The larger the outer diameter of the spiral tube 21, that is, the larger the ratio of the outer diameter of the spiral tube 21 to the inner diameter of the outer tube 10, the longer the circumference of each spiral turn of the spiral tube 21, the longer the overall length of the spiral tube 21, the longer the flow length of the refrigerant, and the greater the heat exchange efficiency of the condenser 100.

[0048] In one embodiment, the diameter of the outer tube 10 is between 15 mm and 100 mm; and / or, the diameter of the straight tube section 22 is between 3 mm and 9.52 mm.

[0049] Specifically, the diameter of the outer tube 10 can be 15mm, 20mm, 25mm, 30mm, 35mm, 40mm, 45mm, 50mm, 55mm, 60mm, 65mm, 70mm, 75mm, 80mm, 85mm, 90mm, 95mm, or 100mm, which can be selected according to the size of the condenser 100 and the heat exchange.

[0050] It should be noted that the larger the diameter of the outer tube 10, the larger the size of the condenser 100, the larger the required containment space, and correspondingly, the greater the theoretical maximum heat exchange that can be achieved.

[0051] Correspondingly, the diameter of the inner tube 20 is smaller than the diameter of the outer tube 10, and its diameter can be 3mm, 3.5mm, 4mm, 4.5mm, 5mm, 5.5mm, 6mm, 6.5mm, 7mm, 7.5mm, 8mm, 8.5mm, 9mm, or 9.5mm.

[0052] It should be noted that the larger the diameter of the inner tube 20, the greater the amount of refrigerant flowing inside, and thus the greater the heat exchange. In practical applications, the specific diameter can be selected based on the size of the condenser 100 and the heat exchange capacity.

[0053] Meanwhile, the outer tube 10 itself should have a considerable height to ensure sufficient heat exchange distance and gravity drop, so that the gas to be condensed can be liquefied and flow down to achieve a better condensation effect.

[0054] In one embodiment, the diameter of the spiral tube 21 is at least five times the diameter of the straight tube section 22. Specifically, the diameter of the spiral tube 21 is approximately 13mm, 15mm, 20mm, 25mm, 30mm, 35mm, 40mm, 45mm, 50mm, 55mm, 60mm, 65mm, 70mm, 75mm, 80mm, 85mm, 90mm, etc.

[0055] The spiral tube 21 is formed by bending a straight tube. The diameter of the spiral tube 21 is set to be at least 5 times the diameter of the straight tube section 22. This ensures that the spiral tube 21 does not collapse during the bending process, thereby ensuring the smooth flow of refrigerant in the inner tube 20.

[0056] It should be noted that, if limited by the size of the condenser 100, the diameter of the spiral tube 21 can be less than 5 times the diameter of the straight tube section 22 and can also be used in the condenser 100. For example, the spiral tube 21 can also be 9mm, 10mm, 11mm, 12mm, etc.

[0057] In one embodiment, the inner tube 20 is made of a smooth tube, or the inner tube 20 is made of an internally threaded tube.

[0058] Specifically, a smooth tube is a tube structure with a smooth inner wall and few or no protrusions. The inner surface of the inner tube 20 made of a smooth tube is also smooth. Because the inner surface of the smooth tube is smooth, the inner tube 20 has less resistance, which is conducive to the flow of refrigerant, thereby increasing the flow speed of refrigerant in the inner tube 20 and reducing the transit time of refrigerant in the inner tube 20.

[0059] An internally threaded tube is a tube structure with raised internal threads on its inner wall surface. The inner tube 20 made of internally threaded tube also has a raised internal thread structure on its inner surface. Compared to an inner tube 20 made of plain tube, the flow resistance of the inner tube 20 made of internally threaded tube is increased. This reduces the flow velocity of the refrigerant in the inner tube 20, thereby increasing the contact time between the refrigerant and the inner tube 20, and thus increasing the heat exchange capacity between the refrigerant and the inner tube 20. Similarly, the inner tube 20 made of internally threaded tube can also increase the contact area between the refrigerant and the inner tube 20, thereby further increasing the heat exchange capacity between the refrigerant and the inner tube 20, that is, enhancing the heat exchange capacity between the refrigerant and the fluid in the outer tube 10.

[0060] It should be noted that, given a fixed length and diameter of the inner tube 20, the heat exchange capacity of an inner tube 20 made with internal threads is greater than that of an inner tube 20 made with a smooth tube. Therefore, in practical applications, the choice between using a smooth tube or an internally threaded tube for the inner tube 20 can be made by comprehensively considering the specifications and dimensions of the inner tube 20 and the outer tube 10, as well as the required heat exchange capacity. Similarly, when using an internally threaded tube for the inner tube 20, given a fixed length and diameter of the inner tube 20, the more turns of the internal thread, the longer the heat exchange length and the greater the heat exchange capacity. Therefore, the number of turns of the internal thread can be designed based on the required heat exchange capacity, taking into account the dimensions of the inner tube 20 and the outer tube 10.

[0061] In one embodiment, the outer tube 10 is made of copper.

[0062] Specifically, copper has good ductility, so the shell tube 11 made of copper also has good ductility. Therefore, when the cone 12 is spun and formed, the good ductility of the shell tube 11 can reduce the difficulty of the spun forming of the cone 12, reduce the equipment requirements for spun forming, and improve the efficiency of spun forming. On the other hand, it can improve the uniformity of the cone 12, thereby improving the overall structural reliability of the outer tube 10 and improving the yield of the outer tube 10.

[0063] Similarly, the inner tube 20 can also be made of copper, which is beneficial for the spiral processing of the inner tube 20, thereby improving the processing efficiency and yield of the inner tube 20.

[0064] Of course, in other embodiments, the outer tube 10 and the inner tube 20 may also be made of other materials, such as carbon steel, low alloy steel, stainless steel, copper, copper-nickel alloy, aluminum alloy, titanium, etc., which are not limited here.

[0065] In one embodiment, a heat insulation mechanism is also included, which is at least circumferentially disposed around the upper part of the outer tube 10.

[0066] Specifically, since the refrigerant enters the spiral tube 21 from the straight section 22 at the upper end of the inner tube 20, and then flows out from the straight section 22 at the lower end of the inner tube 20 after exchanging heat with the high-temperature gas through the spiral tube 21, the temperature of the refrigerant is usually lower than the ambient temperature. Therefore, the temperature at the inflow end of the refrigerant, i.e., the upper end of the inner tube 20, is also lower than the ambient temperature. The straight section 22 at the upper end of the inner tube 20 corresponds to the upper end of the outer tube 10. Therefore, the temperature at the upper end of the outer tube 10 is generally also lower than the ambient temperature. Based on the temperature difference between the upper end of the outer tube 10 and the environment, heat exchange will occur between the two, resulting in heat loss and condensation. Based on this, this embodiment provides an insulation mechanism on the outside of the outer tube 10, and the insulation mechanism covers at least the upper part of the outer tube 10. In this way, the insulation mechanism can isolate the outer tube 10 from the external environment, thereby reducing the energy exchange between the two and preventing heat loss and condensation.

[0067] Optionally, the insulation mechanism may include insulation cotton, which is wrapped around the outside of the outer tube 10 and fixed in place, thus isolating the outer tube 10 from the external environment. The insulation cotton may only cover the upper part of the outer tube 10, or it may cover the entire outer tube 10, depending on the specific needs.

[0068] Optionally, the insulation mechanism may also include a heater located between the insulation cotton and the outer tube 10, and used to regulate the temperature of the insulation cotton to further reduce the energy exchange between the outer tube 10 and the environment, thereby further improving the insulation effect of the insulation mechanism.

[0069] Of course, in other embodiments, the insulation mechanism can also be other structures, such as heating only the coil. This is not a limitation.

[0070] The second aspect of this utility model also provides a refrigeration device, including a condenser 100 of any of the above-described embodiments. The specific structure of the condenser 100 can be referred to the above embodiments. Since the refrigeration device in this embodiment includes the condenser 100 in all the above embodiments, it also has at least the beneficial effects of all the above embodiments, which will not be described in detail here.

[0071] Specifically, refrigeration devices can be air conditioners, refrigerators, distillation towers, etc.

[0072] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this utility model, and are not intended to limit it. Although the utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of this utility model.

Claims

1. A fractionating column, characterized by, The application relates to a condenser, comprising: an outer tube, a sealed central cavity being formed in the outer tube, an air inlet pipe, an air outlet pipe and a condensing pipe being arranged on the outer tube and being communicated with the central cavity, wherein the condensing pipe is arranged at the bottom of the outer tube; an inner tube, the inner tube comprising an integral spiral tube and two straight tube segments arranged at the axial ends of the spiral tube; wherein the spiral tube is arranged in the central cavity, and the two straight tube segments are arranged at the axial ends of the outer tube.

2. The fractionator of claim 1, wherein The outer tube comprises a shell tube and two taper portions connected to the axial ends of the shell tube, and the shell tube and the taper portions are an integral structure.

3. The fractionator of claim 2, wherein, The taper portions are rotationally shrunk and formed.

4. The fractionator of claim 3, wherein The length of the spiral tube is not less than the length of the shell tube; and / or the ratio of the outer diameter of the spiral tube to the inner diameter of the outer tube is not less than 0.

5.

5. The fractionator of claim 1, wherein, The diameter of the outer tube is between 15 mm and 100 mm; and / or the diameter of the straight tube segment is between 3 mm and 9.52 mm.

6. The fractionator of claim 1, wherein The diameter of the spiral tube is at least 5 times the diameter of the straight tube segment.

7. The fractionator of claim 1, wherein The inner tube is made of a smooth tube or an internally threaded tube.

8. The fractionator of claim 1, wherein The material of the outer tube is red copper.

9. The fractionator of claim 1, wherein The application further comprises a heat preservation mechanism, which is arranged at least at the upper part of the outer tube.

10. A refrigeration apparatus characterized by comprising: The application further comprises the condenser according to any one of claims 1-9.

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