Integrated modular four-in-one efficient heat exchanger

Abstract

The invention provides an integrated modular four-in-one efficient heat exchanger, and relates to the technical field of heat exchange equipment, the integrated modular four-in-one efficient heat exchanger comprises a first tube plate, a first shell, a second tube plate and a second shell which are sequentially connected into a whole, the first shell is located at the upper part, and the second shell is located at the lower part; the length extension directions of the first shell and the second shell are the same, and the central axes coincide; the device has the beneficial effects that four functions of pre-cooling, condensation, centrifugal dehydration and filtering dehydration can be realized, and the device has the effects of small size and high separation efficiency; the precooling area and the heating area are integrated in the first shell, so that high-temperature gas entering the first heat transfer pipe can be cooled due to heat exchange with low-temperature gas in the heating area, gas to be exhausted can be heated due to heat exchange with the high-temperature gas in the first heat transfer pipe, and energy is fully utilized. The energy loss is reduced, and the cost is saved.

Description

Technical Field

[0001] The invention relates to the technical field of heat exchange equipment, in particular to an integrated modular four-in-one high-efficiency heat exchanger. Background Art

[0002] A gas heat exchanger is a device used to transfer heat between gases at different temperatures. It is often used in cold dryers to reduce the temperature of compressed air and remove water vapor from the air. It is of great significance in the fields of high-precision industrial manufacturing, medical and health care, food processing, etc. It can provide clean air sources for pneumatic equipment in various industries, protect production equipment, extend the service life of pneumatic equipment, and improve production efficiency. This gas heat exchanger is an indispensable and important component in the post-processing equipment of air compressors.

[0003] There are many patents on gas heat exchangers, such as China Patent Authorization Announcement No. CN217585382U, which discloses a gas cooling heat exchanger, which has a shell, and also includes: an air inlet; an air outlet; a tube bundle assembly connected to the shell and located in the shell, including: a finned heat exchange tube, which is connected to an external cooling water source; a baffle, including: a connecting edge connected to the inner wall of the shell; an air flow edge; an air flow channel opening, which exists between the air flow edge and the inner wall of the shell; wherein the baffles are multiple; there is a spacing distance between adjacent baffles, and the positions of multiple air flow channel openings are staggered; its working method is that the gas is introduced into the shell from the air inlet, and at the same time, the cooling water is introduced into the water inlet cavity from the water inlet and flows in the finned heat exchange tube. During the gas flow process, heat is exchanged with the cooling water in the finned heat exchange tube, so that the water vapor in the gas is condensed into condensed water and condensed in the shell; the processed gas is discharged outward from the air outlet, realizing the drying and dehydration of the gas.

[0004] However, in actual application, it is difficult for the above heat exchanger to fully dry the compressed gas. The cooling and dehydration efficiency of the above-disclosed gas cooling heat exchanger is extremely low, and the dehydration rate is usually no more than 30%, which obviously cannot meet most production needs. In addition, the structure of the traditional mainstream products currently used on the market is a structure in which a precooler, a condenser, and a steam-water separator are separated. It has the disadvantages of bulky size, many consumables, low drying efficiency, and high cost; there are also a few manufacturers that use an integrated heat exchanger made of aluminum. Although it has the advantage of small size, it has the defects of aluminum being not corrosion-resistant, short life, easy to leak, complex products, and long production cycles. That is, there is still room for improvement in the prior art, and it is urgently necessary to disclose a high-efficiency heat exchanger that can overcome the above-mentioned defects to meet current needs. Summary of the invention

[0005] The present invention overcomes the shortcomings of the prior art and provides an integrated modular four-in-one high-efficiency heat exchanger, which simultaneously realizes the four functions of pre-cooling, condensation, centrifugal dehydration and filtration dehydration, has the effects of small size, high separation efficiency and reduced energy loss.

[0006] In order to solve the above technical problems, the present invention is achieved through the following technical solutions: An integrated modular four-in-one high-efficiency heat exchanger comprises a first tube sheet, a first shell, a second tube sheet and a second shell connected in sequence, wherein the first shell is located at the top and the second shell is located at the bottom, and the length extension direction of the first shell and the second shell are the same and the central axis coincides; an end cover is connected to the first tube sheet, and an air inlet pipe is arranged on the end cover; an air outlet pipe is arranged on the first shell; a plurality of first heat transfer pipes for high-temperature gas input are arranged between the first tube sheet and the second tube sheet, and one end of the first heat transfer pipe is gas-connected with the end cover, and the other end of the first heat transfer pipe is gas-connected with the inside of the second shell; the inner wall surrounding area of ​​the first heat transfer pipe forms a pre-cooling area, and the area between the outer wall of the first heat transfer pipe and the inner wall of the first shell forms a temperature rise area; A second heat transfer tube for the flow of refrigerant is arranged in the second shell, and the second heat transfer tube is arranged in an integral winding shape around the central axis of the second shell; a hollow tube is coaxially arranged in the second shell, and the hollow tube is connected to the second tube sheet; the inner wall of the hollow tube surrounds the area to form a reflux zone, and the reflux zone is connected to the temperature rise zone by gas communication, and the area between the outer wall of the hollow tube and the inner wall of the second shell forms a condensation zone, and a spiral guide plate is also arranged in the condensation zone, and the second heat transfer tube is connected and fixed on the spiral guide plate; the hollow tube, the spiral guide plate and the inner wall of the second shell surround a spiral channel, and the gas transported from the first heat transfer tube to the second shell enters the spiral channel and is transported to the entrance of the hollow tube. When the gas is transported in the spiral channel, it connects with the second heat transfer tube to condense and cool down and dehydrate, and at the same time flows along the spiral channel to undergo centrifugal motion and dehydrate; The high-temperature gas enters from the air inlet pipe, and when flowing through the pre-cooling zone, it exchanges heat with the cooled gas in the heating zone to be pre-cooled. Then, when continuing to flow to the condensation zone, it exchanges heat with the second heat transfer pipe with refrigerant to be cooled and dehydrated, and centrifugal movement and dehydration occur at the same time. Finally, it flows back along the hollow pipe to the heating zone, exchanges heat with the high-temperature gas flowing in from the first heat transfer pipe, and is heated and discharged from the air outlet pipe.

[0007] Furthermore, a gas-water separation component is provided at the bottom of the second shell below the hollow tube, and the gas flowing out of the spiral channel passes through the gas-water separation component from top to bottom, and after being reflected by the inner wall of the bottom of the second shell, passes through the gas-water separation component from bottom to top and enters the hollow tube.

[0008] Furthermore, the inner wall of the first heat transfer tube is provided with petal-shaped fins to increase the heat transfer area of ​​the gas in the first heat transfer tube; the calculation formula of the heat transfer coefficient of the fluid in the first heat transfer tube conforms to the following: ,in, is the heat transfer coefficient of the fluid in the tube, and its unit is w / (㎡×℃); is the inner diameter of the first heat transfer tube, in m; is the flow rate of the fluid in the pipe, and its unit is m / s; is the viscosity of the fluid in the tube, its unit is Pa×s; is the tube fluid density, its unit is Kg / m 3 ; is the thermal conductivity of the fluid in the tube, and its unit is w / (m×℃); It is the constant-pressure specific heat of the fluid in the tube, and its unit is KJ / (kg×℃); n is a constant.

[0009] Furthermore, a plurality of parallel fins are longitudinally and equidistantly arranged in the first shell, a first gas flow hole is opened in the middle of the fin, a horizontal flow channel is formed between adjacent fins, and the first heat transfer tube is vertically expanded on the fin; the fin increases the heat transfer area of ​​the gas; a plurality of concave and convex points are arranged on the fin to cause disturbance and turbulence of the gas, destroy the boundary layer, and be more conducive to heat transfer; A first baffle plate and a second baffle plate are arranged between the fins, the first baffle plate and the second baffle plate are arranged at intervals, the first baffle plate is arranged in a circular ring shape, a second gas flow hole is opened in the middle of the first baffle plate, the second baffle plate is arranged in a circular shape, the diameter of the first baffle plate is greater than the diameter of the second baffle plate, the edge of the first baffle plate is sealed and connected to the inner wall of the first shell, and a gas flow gap is reserved between the edge of the second baffle plate and the inner wall of the first shell, so that the temperature rise zone (B ) flows in an arcuate shape along the horizontal flow channel, the first gas flow hole, the second gas flow hole and the gas flow gap under the obstruction of the first baffle plate and the second baffle plate; through holes for installing the first heat transfer tube are provided on the first baffle plate and the second baffle plate; by increasing the heat transfer area inside and outside the first heat transfer tube, the heat transfer boundary layer is destroyed, and the Reynolds number is increased, thereby greatly improving the total heat transfer coefficient of the system. The total heat transfer coefficient K0 and the heat exchange power Q meet the following formula: Among them, S is the total heat transfer area, unit is ㎡; Q is the heat transfer power, unit is kcal / h; K0 is the total heat transfer coefficient, unit is w / (㎡×℃); is the logarithmic mean temperature difference, its unit is ℃; in the heat transfer power Q and logarithmic mean temperature difference Under the premise of unchanged, the greater the total heat transfer coefficient, the smaller the required heat exchange area; that is, the greater the total heat transfer coefficient K0, the more compact the product is, which is conducive to saving space and cost.

[0010] Furthermore, the second shell is cylindrical, one side edge of the spiral guide plate is connected to the hollow tube, and the other side edge of the spiral guide plate is connected to the inner wall of the second shell, so as to make the gas flow smoothly, eliminate the heat exchange dead corner, and reduce the airflow resistance; the second shell is provided with a refrigerant inlet pipe and a refrigerant outlet pipe, one end of the refrigerant inlet pipe is connected to the second heat transfer pipe, and the other end of the second heat transfer pipe is connected to the refrigerant outlet pipe; the outer wall of the second heat transfer pipe is rolled with threaded fins to increase the heat transfer area with the gas.

[0011] Furthermore, the gas-water separation component includes five or more layers of stainless steel filter screens stacked together, and the stainless steel filter screens have a mesh size of 50 or more to capture and separate tiny water droplets, thereby allowing the gas-water separation to be more complete.

[0012] Furthermore, a drain outlet is provided at the bottom of the second shell, and a guide plate is provided at the inner bottom end of the second shell. The guide plate is located below the condensation area, a hydrophobic gap is maintained between the edge of the guide plate and the inner wall of the second shell, and the upper surface of the guide plate forms an arched shape with a high middle portion and low surrounding portions.

[0013] Furthermore, the cross-sectional diameters of the first shell and the second shell are the same, the first tube sheet and the second tube sheet are the same in size and overlap longitudinally, and the horizontal projection areas of the first shell and the second shell are within the second tube sheet.

[0014] Furthermore, the first tube sheet and the second tube sheet are both provided with tube holes, and the two ends of the first heat transfer tube are correspondingly connected to the tube holes of the first tube sheet and the second tube sheet; the end cover is arranged in a trumpet expansion shape from the air inlet pipe toward the first tube sheet.

[0015] Compared with the prior art, the present invention has the following beneficial effects: This high-efficiency heat exchanger can realize four functions: precooling, condensation, centrifugal dehydration and filtration dehydration. It is a combined structure with small size, low cost and high separation efficiency. This modular design has few specifications and universal design for large and small machines, which is easy to mass produce. Here, the precooling zone and the heating zone are integrated in the first shell, so the high-temperature gas entering the first heat transfer tube will cool down due to heat exchange with the low-temperature gas in the heating zone, and the gas to be discharged will heat up due to heat exchange with the high-temperature gas in the first heat transfer tube to meet the use requirements, so that energy can be fully utilized, energy loss can be reduced, and cost can be saved. The components of this high-efficiency heat exchanger have good corrosion resistance and sealing, and the product has a long service life. In addition, multiple means such as condensation, centrifugal dehydration and filtration dehydration are adopted to make the gas condensation and drying effect good, and the gas moisture removal rate is very high. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] The accompanying drawings are used to provide a further understanding of the present invention and are used together with the embodiments of the present invention to explain the present invention, but do not constitute a limitation of the present invention. In the accompanying drawings: Figure 1 The three-dimensional high-efficiency heat exchanger of the present invention Figure 1 ; Figure 2 The three-dimensional high-efficiency heat exchanger of the present invention Figure 2 , remove the end cap; Figure 3 is a cross-sectional view of the high-efficiency heat exchanger of the present invention; Figure 4 It is a schematic diagram of the internal structure of the high-efficiency heat exchanger of the present invention; Figure 5 is an enlarged view of the internal structure of the high-efficiency heat exchanger located at the lower part; Figure 6 is a schematic diagram of a cross-sectional view of the high-efficiency heat exchanger of the present invention located at an upper portion; Figure 7 is a schematic diagram of a cross-sectional view of the high-efficiency heat exchanger of the present invention located at the lower part; Figure 8 It is a schematic diagram of a first baffle plate and a second baffle plate of the high-efficiency heat exchanger of the present invention; Fig. 9 It is a structural schematic diagram of the fins of the high-efficiency heat exchanger described in the present invention, and the fins have concave and convex points.

[0017] Fig.10 It is a structural schematic diagram of the hollow tube and spiral guide plate of the high-efficiency heat exchanger of the present invention; Fig.11 It is a schematic diagram of a first heat transfer tube of the high-efficiency heat exchanger of the present invention having petal-shaped fins.

[0018] In the figure: 1, first tube sheet; 101, tube hole; 2, first shell; 3, second tube sheet; 4, second shell; 5, end cover; 6, air inlet pipe; 7, air outlet pipe; 8, first heat transfer pipe; 9, second heat transfer pipe; 10, hollow pipe; 11, spiral guide plate; 12, gas-water separation component; 13, fin; 1301, first gas flow hole; 14, first baffle plate; 1401, second gas flow hole; 15, second baffle plate; 16, through hole; 17, refrigerant inlet pipe; 18, refrigerant outlet pipe; 19, drain port; 20, guide plate; A. Pre-cooling zone; B. Heating zone; C. Reflux zone; D. Condensation zone. DETAILED DESCRIPTION

[0019] The preferred embodiments of the present invention are described below in conjunction with the accompanying drawings. It should be understood that the preferred embodiments described herein are only used to illustrate and explain the present invention, and are not used to limit the present invention.

[0020] like Figures 1 to 9 As shown, the present invention requests protection for an integrated modular four-in-one high-efficiency heat exchanger. Since most of the equipment currently on the market for gas heat exchange, such as cold dryers, adopt a split type to achieve air drying, which has the defects of bulky size, many consumables and high cost, the present application discloses such a heat exchange equipment which can realize multiple functions of pre-cooling, condensation and gas-water separation in one, and has the advantages of small size, high separation efficiency, reduced energy loss and cost saving.

[0021] The integrated modular four-in-one high-efficiency heat exchanger includes a first tube sheet 1, a first shell 2, a second tube sheet 3 and a second shell 4 which are connected in sequence. The first shell 2 is located at the top and the second shell 4 is located at the bottom. When in use, they are placed upright, that is, the second shell 4 is physically located at the bottom and the first shell 2 is physically located at the top. The length extension direction of the first shell 2 and the second shell 4 is the same and the central axis coincides, making the structure compact and regular.

[0022] The first tube sheet 1 is connected with an end cover 5, on which an air inlet pipe 6 is arranged; the first shell 2 is provided with an air outlet pipe 7; a plurality of first heat transfer pipes 8 for high-temperature gas input are arranged between the first tube sheet 1 and the second tube sheet 3 and are distributed around the central axis of the first shell 2, one end of the first heat transfer pipe 8 is gas-connected with the end cover 5, and the other end of the first heat transfer pipe 8 is gas-connected with the inside of the second shell 4; specifically, the first tube sheet 1 and the second tube sheet 3 are both provided with tube holes 101, and the two ends of the first heat transfer pipe 8 are correspondingly connected to the tube holes 101 of the first tube sheet 1 and the second tube sheet 3, and the first heat transfer pipe 8 can be fixedly connected to the tube hole 101 by a tube expansion process; the high-temperature compressed gas enters the end cover 5 through the air inlet pipe 6 and flows into the first heat transfer pipe 8.

[0023] Combination Figure 1 as well as Figure 6 It can be seen that the end cover 5 is configured to expand in a trumpet shape from the air inlet pipe 6 toward the first tube sheet 1, and the inner wall of the end cover 5 is also in a trumpet shape. This design not only helps the gas entering from the air inlet pipe 6 to be dispersed and flow into each first heat transfer tube 8, but also helps to enhance the smooth flow of the gas, avoid the existence of heat exchange dead corners, and reduce airflow resistance.

[0024] A second heat transfer tube 9 for the flow of refrigerant is arranged in the second shell 4. The second heat transfer tube 9 is arranged in an integral winding shape around the central axis of the second shell 4. The integral winding shape helps to lengthen the length of the second heat transfer tube 9 in the second shell 4, that is, to increase the heat exchange area between the second heat transfer tube 9 and the gas, thereby improving the heat exchange effect. A refrigerant inlet pipe 17 and a refrigerant outlet pipe 18 are arranged on the second shell 4. One end of the refrigerant inlet pipe 17 is connected to the second heat transfer tube 9, and the other end of the second heat transfer tube 9 is connected to the refrigerant outlet pipe 18. In this embodiment, the refrigerant is mainly Freon. The second heat transfer tube 9 is for the flow of Freon. The gas enters the second shell 4 from the first heat transfer tube 8 and is condensed by connecting with the second heat transfer tube 9, so that the gas is cooled and dehydrated. The outer wall of the second heat transfer tube 9 is rolled with threaded fins to increase the heat transfer area with the gas and improve the heat exchange effect. In the condensation, the gas will be cooled to below the dew point, thereby releasing the moisture in the gas.

[0025] It has been verified in practice that by rolling threaded fins on the outer wall of the second heat transfer tube 9, the heat transfer area can be more than 2.6 times that of a plain tube, and the heat transfer area is increased by more than 18% compared with a traditional copper threaded fin tube under the same conditions.

[0026] A hollow tube 10 is coaxially arranged in the second shell 4, and the hollow tube 10 is connected to the second tube sheet 3; the inner wall surrounding area of ​​the first heat transfer tube 8 is set to form a pre-cooling zone A, and the area between the outer wall of the first heat transfer tube 8 and the inner wall of the first shell 2 forms a heating zone B; the inner wall surrounding area of ​​the hollow tube 10 forms a reflux zone C, and the area between the outer wall of the hollow tube 10 and the inner wall of the second shell 4 forms a condensation zone D, and the reflux zone C is gas-connected with the heating zone B. In this heat exchanger, the gas flow path is the pre-cooling zone A, the heating zone B, the condensation zone D, and the reflux zone C; the condensation zone D is also provided with a spiral guide plate 11, and the second heat transfer tube 9 is fixedly connected to the spiral guide plate 11.

[0027] The spiral guide plate 11 has at least the following two functions: First, the spiral guide plate 11, the hollow tube 10, and the inner wall of the second shell 4 form a spiral channel, so that the gas transported from the first heat transfer tube 8 to the second shell 4 enters the spiral channel and is transported to the entrance of the hollow tube 10. On the one hand, the gas is connected with the second heat transfer tube 9 during the spiral channel, condenses and cools down and dehydrates, and at the same time flows along the spiral channel and dehydrates by centrifugal motion, that is, it has two dehydration functions in the process of circulating in the spiral channel. Second, the spiral guide plate 11 is provided with a through hole for the installation of the second heat transfer tube 9, that is, the spiral guide plate 11 has a certain fixing effect on the second heat transfer tube 9, which enhances the stability of the structure.

[0028] In this embodiment, the second shell 4 is cylindrical, one side edge of the spiral guide plate 11 is connected to the hollow tube 10, and the other side edge of the spiral guide plate 11 is connected to the inner wall of the second shell 4. The structure is compact, that is, the spiral channel formed has a high sealing property, so that the gas can only flow along the spiral channel. The second shell 4 is designed in a cylindrical shape, and its inner wall is also cylindrical and quite smooth, that is, the gas will not encounter any obstructions such as corners or steps during the flow, thereby making the gas flow smoothly, eliminating heat exchange dead corners, and reducing airflow resistance.

[0029] The heat exchange process of the gas is that the high-temperature gas enters from the air inlet pipe 6, exchanges heat with the gas cooled in the temperature rising zone B when flowing through the pre-cooling zone A, and is pre-cooled. Then, when continuing to flow to the condensation zone D, it exchanges heat with the second heat transfer tube 9 through which the refrigerant passes, and is cooled and dehydrated. At the same time, centrifugal movement and dehydration occur. Finally, it flows back to the temperature rising zone B along the hollow tube 10, exchanges heat with the high-temperature gas flowing in from the first heat transfer tube 8, and is discharged from the air outlet pipe 7 after being heated.

[0030] In this embodiment, in order to enhance the dehydration effect, a gas-water separation component 12 is provided at the bottom of the second shell 4 below the hollow tube 10. The gas flowing out of the spiral channel passes through the gas-water separation component 12 from top to bottom, and after being reflected by the inner wall of the bottom of the second shell 4, passes through the gas-water separation component 12 from bottom to top and enters the hollow tube 10.

[0031] The spiral guide plate 11 allows the gas to follow a spiral path, thereby achieving preliminary gas-water separation; it can also eliminate heat exchange dead corners, allowing heat exchange to be more complete; and reduce airflow resistance.

[0032] In actual experiments, under the premise of the same heat exchange effect, the use of spiral guide plates can save more than 22% of heat exchange area compared with ordinary arcuate baffles. That is, the use of the spiral guide plate 11 structure saves more materials.

[0033] By rolling threaded fins on the outer wall of the second heat transfer tube 9 and using a spiral guide plate 11, not only the heat transfer area is increased, but also the fluid resistance is reduced through structural optimization, gas-water separation is achieved, the overall heat transfer coefficient between the refrigerant and the compressed gas is increased, the product volume is reduced, and the product cost is reduced.

[0034] A drain port 19 is provided at the bottom of the second shell 4 , and a drain valve is connected to the drain port 19 , which only drains water but not gas. Therefore, the gas flowing out of the spiral channel will only be transported to the temperature rising zone B along the hollow tube 10 .

[0035] In practical applications, the temperature of the high-temperature gas entering from the air inlet pipe 6 is generally 90-100°C, and the temperature of the dehydrated gas we ultimately need is 50-60°C, but the gas after precooling and condensation may be at 10-20°C. Therefore, in this heat exchanger, the condensed and dehydrated gas is returned to the temperature rising zone B through the hollow tube 10, and is heated by heat exchange with the high-temperature gas flowing in from the first heat transfer tube 8 and then discharged from the air outlet pipe 7; and the high-temperature gas from the first heat transfer tube 8 is cooled by heat exchange with the low-temperature gas in the temperature rising zone B, and is initially cooled, that is, the high-temperature gas and the low-temperature gas are each used as needed, so that energy is fully utilized, energy loss is reduced, and cost is saved.

[0036] In this embodiment, the inner wall of the first heat transfer tube 8 is provided with petal-shaped fins to increase the heat transfer area of ​​the gas in the first heat transfer tube 8; the calculation formula of the heat transfer coefficient of the fluid in the first heat transfer tube 8 conforms to the following: in, is the heat transfer coefficient of the fluid in the tube, and its unit is w / (㎡×℃); is the inner diameter of the first heat transfer tube, in m; is the flow rate of the fluid in the pipe, and its unit is m / s; is the viscosity of the fluid in the tube, its unit is Pa×s; is the density of the fluid in the tube, and its unit is Kg / m 3 ; is the thermal conductivity of the fluid in the tube, and its unit is w / (m×℃); It is the constant-pressure specific heat of the fluid in the tube, and its unit is KJ / (kg×℃); n is a constant.

[0037] According to the research of the inventor, petal-shaped fins are provided on the inner wall of the first heat transfer tube 8, and the heat transfer area of ​​the gas in the first heat transfer tube 8 is increased by more than 1.5 times compared with that of a plain tube.

[0038] like Figure 6As shown, a plurality of parallel fins 13 are longitudinally equidistantly arranged in the first shell 2, a first gas flow hole 1301 is opened in the middle of the fin 13, and a horizontal flow channel is formed between adjacent fins 13, and the first heat transfer tube 8 is vertically expanded on the fin 13; that is, the high-temperature gas entering the first heat transfer tube 8 will transfer the temperature to the fin 13 for dissipation, and the fin 13 increases the heat transfer area of ​​the gas; in addition, a plurality of concave and convex points are arranged on the fin 13 to cause disturbance and turbulence of the gas, destroy the boundary layer, and be more conducive to heat transfer; the first heat transfer tube 8 adds concave and convex points to the fin 13, so that the heat transfer area of ​​the fin 13 can reach more than 5 times that of the light tube; the heat transfer area of ​​the fin 13 can reach more than 2.5 times that of the traditional threaded tube.

[0039] In this embodiment, a first deflection baffle 14 and a second deflection baffle 15 are arranged between the fins 13, the first deflection baffle 14 and the second deflection baffle 15 are arranged at intervals, the first deflection baffle 14 is arranged in a circular shape, a second gas flow hole 1401 is opened in the middle of the first deflection baffle 14, the second deflection baffle 15 is arranged in a circular shape, the diameter of the first deflection baffle 14 is greater than the diameter of the second deflection baffle 15, the edge of the first deflection baffle 14 is sealed and connected to the inner wall of the first shell 2, and the edge of the second deflection baffle 15 is sealed and connected to the inner wall of the first shell 2. A gas flow gap is reserved between the fins 13 and the fins 13, that is, the gas can only flow through the first gas flow hole 1301, the second gas flow hole 1401, the gas flow gap and the horizontal flow channel between the adjacent fins 13 during the flow process in the temperature rising zone B, so that the gas in the temperature rising zone B flows along the horizontal flow channel, the first gas flow hole 1301, the second gas flow hole 1401 and the gas flow gap in an arc shape under the obstruction of the first deflection baffle 14 and the second deflection baffle 15, which helps to extend the flow path and enhance the contact area with the fin 13 during flow; plus from Figure 6 It can be seen that the fins 13 are arranged in parallel, which means that the gas flows horizontally in the horizontal flow channel, so that the gas flow path can be as long as possible in a limited height space, and the heat exchange efficiency is high; in other words, this structure helps to reduce the height of the first shell 2, making the overall structure small and compact, saving manufacturing costs.

[0040] The first baffle plate 14 and the second baffle plate 15 are both provided with through holes 16 for installing the first heat transfer tube 8 , that is, the provision of the first baffle plate 14 and the second baffle plate 15 also helps to enhance the fixing effect of the first heat transfer tube 8 .

[0041] By increasing the heat transfer area both inside and outside the first heat transfer tube 8, the heat transfer boundary layer is destroyed and the Reynolds number is increased, thereby greatly improving the total heat transfer coefficient of the system. The total heat transfer coefficient K0 and the heat transfer power Q meet the following formula: Among them, S is the total heat transfer area, unit is ㎡; Q is the heat transfer power, unit is kcal / h; K0 is the total heat transfer coefficient, unit is w / (㎡×℃); is the logarithmic mean temperature difference, its unit is ℃; in the heat transfer power Q and logarithmic mean temperature difference Under the premise of unchanged, the greater the total heat transfer coefficient, the smaller the required heat exchange area; that is, the greater the total heat transfer coefficient K0, the more compact the product is, which is conducive to saving space and cost.

[0042] In this embodiment, the gas-water separation component 12 includes five or more layers of stainless steel filter screens stacked together, and the stainless steel filter screens have a mesh size of 50 or more to capture and separate tiny water droplets, thereby allowing the gas-water separation to be more complete.

[0043] The gas-water separation component 12 is close to the lower end opening of the hollow tube 10, so that the gas flowing out of the spiral channel can pass through the gas-water separation component 12 downward, and then pass through the gas-water separation component 12 upward to enter the hollow tube 10 after being reflected by the bottom of the second shell 4. The gas can be filtered twice, which is more conducive to removing water droplets.

[0044] In this embodiment, the water is first roughly separated in the condensation zone D through condensation and centrifugal gas-water separation, which has a relatively high efficiency; then the gas-water separation component 12 uses a multi-layer filter screen to perform physical gas-water separation, which can capture and separate tiny water droplets, thereby allowing the gas-water separation to be more complete.

[0045] The present invention adopts a structure combining centrifugal and filter-type air-water separation, which helps to improve the water removal rate and can meet the occasions with higher requirements on the purity of compressed air.

[0046] A drain port 19 is provided at the bottom of the second shell 4, and a guide plate 20 is provided at the inner bottom end of the second shell 4. The guide plate 20 is located below the condensation zone D. A hydrophobic gap is maintained between the edge of the guide plate 20 and the inner wall of the second shell 4. Since water droplets are generated during heat exchange between the low-temperature second heat transfer tube 9 and the gas in the condensation zone D, when the water droplets fall onto the guide plate 20, they will eventually stay in the drain port 19 along the hydrophobic gap around the guide plate 20. In this embodiment, the upper surface of the guide plate 20 is formed with an arch shape with a high middle part and low surroundings, which helps the water droplets falling onto the guide plate 20 to slide around without forming water accumulation.

[0047] In this embodiment, the cross-sectional diameters of the first shell 2 and the second shell 4 are the same, the first tube sheet 1 and the second tube sheet 3 are the same size and overlap longitudinally, and the horizontal projection areas of the first shell 2 and the second shell 4 are within the second tube sheet 3, that is, the area of ​​the second tube sheet 3 is larger than the cross-sectional areas of the first shell 2 and the second shell 4, thereby facilitating the edges of the first shell 2 and the second shell 4 to be sealed and connected to the first tube sheet 1 and the second tube sheet 3.

[0048] The present invention provides an integrated modular four-in-one high-efficiency heat exchanger that can realize four functions of pre-cooling, condensing, centrifugal dehydration and filtering dehydration for high-temperature gas, and has the effects of small volume and high separation efficiency; here, the pre-cooling zone A and the heating zone B are integrated in the first shell 2, so the high-temperature gas entering the first heat transfer tube 8 will be cooled due to heat exchange with the low-temperature gas in the heating zone B, and the gas to be discharged will be heated due to heat exchange with the high-temperature gas in the first heat transfer tube 8 to meet the use requirements, so that energy can be fully utilized, energy loss is reduced, and cost is saved.

[0049] Finally, it should be noted that the above are only preferred embodiments of the present invention and are not intended to limit the present invention. Although the present invention has been described in detail with reference to the embodiments, those skilled in the art can still modify the technical solutions described in the aforementioned embodiments or make equivalent substitutions for some of the technical features therein. However, any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. Integrated modular four-in-one high-efficiency heat exchanger, characterized by: The invention comprises a first tube sheet (1), a first shell (2), a second tube sheet (3) and a second shell (4) which are connected in sequence and integrated into one body, the first shell (2) being located at the top and the second shell (4) being located at the bottom, the length extension direction of the first shell (2) and the second shell (4) being the same and the central axis thereof coinciding with each other; an end cover (5) being connected to the first tube sheet (1), an air inlet pipe (6) being arranged on the end cover (5); an air outlet pipe (7) being arranged on the first shell (2); a plurality of first heat transfer tubes (8) for inputting high-temperature gas being arranged and distributed around the central axis of the first shell (2) being arranged between the first tube sheet (1) and the second tube sheet (3), one end of the first heat transfer tube (8) being in gas communication with the end cover (5), and the other end of the first heat transfer tube (8) being in gas communication with the inside of the second shell (4); an area surrounded by the inner wall of the first heat transfer tube (8) forming a pre-cooling area (A), and an area between the outer wall of the first heat transfer tube (8) and the inner wall of the first shell (2) forming a temperature rising area (B); A second heat transfer tube (9) for the flow of refrigerant is arranged in the second shell (4), and the second heat transfer tube (9) is arranged in an integral winding shape around the central axis of the second shell (4); a hollow tube (10) is coaxially arranged in the second shell (4), and the hollow tube (10) is connected to the second tube sheet (3); the area surrounded by the inner wall of the hollow tube (10) forms a reflux zone (C), the reflux zone (C) is gas-connected to the temperature rising zone (B), and the area between the outer wall of the hollow tube (10) and the inner wall of the second shell (4) forms a condensation zone (D). The condensation zone (D) is further provided with a spiral guide plate (11), and the second heat transfer tube (9) is connected and fixed to the spiral guide plate (11); the hollow tube (10), the spiral guide plate (11) and the inner wall of the second shell (4) surround and form a spiral channel, and the gas transported from the first heat transfer tube (8) to the second shell (4) enters the spiral channel and is transported to the entrance of the hollow tube (10). When the gas is transported in the spiral channel, it contacts the second heat transfer tube (9) and condenses to reduce temperature and dehydrate, and at the same time flows along the spiral channel to cause centrifugal movement and dehydration; The high-temperature gas enters from the air inlet pipe (6), and when flowing through the pre-cooling zone (A), it exchanges heat with the gas cooled in the heating zone (B) to be pre-cooled. Then, when continuing to flow to the condensation zone (D), it exchanges heat with the second heat transfer tube (9) through which the refrigerant passes to be cooled and dehydrated. At the same time, centrifugal movement and dehydration occur. Finally, it flows back to the heating zone (B) along the hollow tube (10), exchanges heat with the high-temperature gas flowing in from the first heat transfer tube (8), and is heated before being discharged from the air outlet pipe (7).

2. The integrated modular four-in-one high-efficiency heat exchanger according to claim 1 is characterized in that: A gas-water separation component (12) is provided at the bottom of the second shell (4) below the hollow tube (10); the gas flowing out of the spiral channel passes through the gas-water separation component (12) from top to bottom, is reflected by the inner wall of the bottom of the second shell (4), and then passes through the gas-water separation component (12) from bottom to top into the hollow tube (10).

3. The integrated modular four-in-one high-efficiency heat exchanger according to claim 1 is characterized in that: The inner wall of the first heat transfer tube (8) is provided with petal-shaped fins to increase the heat transfer tube area of ​​the gas in the first heat transfer tube (8); the calculation formula of the heat transfer coefficient of the fluid in the first heat transfer tube (8) conforms to the following: in, is the heat transfer coefficient of the fluid in the tube, and its unit is w / (㎡×℃); is the inner diameter of the first heat transfer tube, in m; is the flow rate of the fluid in the pipe, and its unit is m / s; is the viscosity of the fluid in the tube, its unit is Pa×s; is the density of the fluid in the tube, and its unit is Kg / m 3 ; is the thermal conductivity of the fluid in the tube, and its unit is w / (m×℃); It is the constant-pressure specific heat of the fluid in the tube, and its unit is KJ / (kg×℃); n is a constant.

4. The integrated modular four-in-one high-efficiency heat exchanger according to claim 3 is characterized in that: A plurality of parallel fins (13) are longitudinally equidistantly arranged in the first shell (2); a first gas flow hole (1301) is provided in the middle of the fin (13); a horizontal flow channel is formed between adjacent fins (13); and the first heat transfer pipe (8) is vertically expanded on the fin (13); the fin (13) is used to increase the heat transfer area of ​​the gas; and a plurality of concave and convex points are provided on the fin (13) to cause disturbance and turbulence in the gas, thereby destroying the boundary layer and being more conducive to heat transfer; A first deflection baffle (14) and a second deflection baffle (15) are arranged between the fins (13); the first deflection baffle (14) and the second deflection baffle (15) are arranged at an interval; the first deflection baffle (14) is arranged in a circular ring shape; a second gas flow hole (1401) is opened in the middle of the first deflection baffle (14); the second deflection baffle (15) is arranged in a circular shape; the diameter of the first deflection baffle (14) is greater than the diameter of the second deflection baffle (15); the edge of the first deflection baffle (14) is in contact with the first shell (2); The first shell (2) is sealedly connected to the inner wall of the second baffle plate (15), and a gas flow gap is reserved between the edge of the second baffle plate (15) and the inner wall of the first shell (2), so that the gas in the temperature rising zone (B) flows in an arcuate shape along the horizontal flow channel, the first gas flow hole (1301), the second gas flow hole (1401), and the gas flow gap under the obstruction of the first baffle plate (14) and the second baffle plate (15); the first baffle plate (14) and the second baffle plate (15) are both provided with a through hole (16) for mounting the first heat transfer pipe (8); By increasing the heat transfer area both inside and outside the first heat transfer tube (8), the heat transfer boundary layer is destroyed and the Reynolds number is increased, thereby greatly improving the total heat transfer coefficient of the system. The total heat transfer coefficient K0 and the heat transfer power Q meet the following formula: Among them, S is the total heat transfer area, unit is ㎡; Q is the heat transfer power, unit is kcal / h; K0 is the total heat transfer coefficient, unit is w / (㎡×℃); is the logarithmic mean temperature difference, its unit is ℃; in the heat transfer power Q and logarithmic mean temperature difference Under the premise of unchanged, the greater the total heat transfer coefficient, the smaller the required heat exchange area.

5. The integrated modular four-in-one high-efficiency heat exchanger according to any one of claims 1 to 4, characterized in that: The second shell (4) is cylindrical, one side edge of the spiral guide plate (11) is connected to the hollow tube (10), and the other side edge of the spiral guide plate (11) is connected to the inner wall of the second shell (4); the second shell (4) is provided with a refrigerant inlet pipe (17) and a refrigerant outlet pipe (18), one end of the refrigerant inlet pipe (17) is connected to the second heat transfer pipe (9), and the other end of the second heat transfer pipe (9) is connected to the refrigerant outlet pipe (18); the outer wall of the second heat transfer pipe (9) is rolled with threaded fins.

6. The integrated modular four-in-one high-efficiency heat exchanger according to claim 5 is characterized in that: The gas-water separation component (12) comprises five or more layers of stainless steel filter screens stacked together, and the stainless steel filter screens are usually 50 meshes or larger.

7. The integrated modular four-in-one high-efficiency heat exchanger according to claim 1 is characterized in that: The bottom of the second shell (4) is provided with a drainage port (19), and the inner bottom end of the second shell (4) is provided with a guide plate (20), the guide plate (20) being located below the condensation zone (D), a hydrophobic gap being maintained between the edge of the guide plate (20) and the inner wall of the second shell (4), and the upper surface of the guide plate (20) is formed into an arched shape with a high middle portion and low surrounding portions to facilitate drainage.

8. The integrated modular four-in-one high-efficiency heat exchanger according to claim 1 is characterized in that: The cross-sectional diameters of the first shell (2) and the second shell (4) are the same, and the first tube sheet (1) and the second tube sheet (3) are the same in size and overlap in the longitudinal direction.

9. The integrated modular four-in-one high-efficiency heat exchanger according to claim 8, characterized in that: The first tube sheet (1) and the second tube sheet (3) are both provided with tube holes (101), and the two ends of the first heat transfer tube (8) are correspondingly connected to the tube holes (101) of the first tube sheet (1) and the second tube sheet (3); the end cover (5) is arranged in a trumpet expansion shape from the air inlet pipe (6) toward the first tube sheet (1).

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