Evaporation and overheating integrated heat exchanger and superheated steam generation method

Abstract

The invention discloses an evaporation and overheating integrated heat exchanger and a superheated steam generation method.The heat exchanger comprises a horizontal shell and a partition plate arranged in the shell and provided with evaporation holes, the partition plate divides the shell into an evaporation cavity and an overheating cavity, and a first heating assembly is arranged in the evaporation cavity of the shell; the second heating assembly is arranged in the overheating cavity of the shell, and the liquid inlet and the steam outlet are formed in the upper portion and the lower portion of the same end of the shell. During use, water is guided into the evaporation cavity through the liquid inlet; starting the first heating assembly and the second heating assembly; the first heating assembly is used for heating water in the evaporation cavity to generate steam; steam enters the overheating cavity through the evaporation holes and is output through the steam outlet after being heated into superheated steam by the second heating assembly. The device is small in occupied area, compact in structure and small in pressure loss in the steam evaporation process; the partition plate is creatively used as the gas-liquid separator, and an independent gas-liquid separator is not needed. Therefore, the evaporation efficiency is high, and the quality of the generated steam is good.

Description

Technical Field

[0001] The present invention belongs to the field of machinery, and relates to a heat exchange device, in particular to an integrated evaporation and superheating heat exchanger and a method for generating superheated steam. Background Art

[0002] Shell-and-tube heat exchange devices for liquid evaporation and superheating are included in various industries such as metallurgy, pharmaceuticals, chemicals, and energy. Usually, the evaporation and superheating of liquids are divided into three devices, namely: a preheater, an evaporator, and a superheater. The three devices are interconnected through pipelines, which not only occupy a large amount of space but also have a relatively high cost. With the development of high-efficiency heat exchanger technology, more and more application scenarios of shell-and-tube heat exchange devices have put forward requirements for the integration, cost, and pressure loss of the devices. However, there is less research on integrated heat exchangers at present, and there are obvious deficiencies in the system integration and system of the three devices.

[0003] The prior art CN111912260A discloses a heat exchange device integrating preheating, evaporation, and superheating, including: a shell and heat exchange tubes located inside the shell. The internal space of the shell of the heat exchange device is divided into a preheating section, an evaporation section, and a superheating section. The preheating section and the evaporation section are separated by a first partition, and the evaporation section and the superheating section are separated by a second partition. The first partition and the second partition are arranged in parallel with each other, and the two are fixedly supported by a plurality of partition support plates. The inlet of the preheating section is communicated with the inlet of the shell, the outlet of the preheating section is communicated with the inlet of the evaporation section, a plurality of mutually parallel preheating baffles are uniformly arranged inside the preheating section along the flow direction of the working medium, a vapor-liquid separation device is arranged on the second partition, and the vapor-liquid separation device is used for separating the vapor-liquid mixed working medium in the evaporation section. A plurality of mutually parallel superheating baffles are uniformly arranged inside the superheating section along its length direction, and the outlet of the superheating section is communicated with the outlet of the shell.

[0004] The integrated heat exchanger of CN111912260A integrating a preheater, an evaporator, and a superheater improves the integration of the heat exchange device; at the same time, partitions are added to the structure, which can effectively distinguish each functional area and improve the versatility of the device. Integrating the three devices into one effectively reduces the pressure loss on the shell side, reduces the weight of the total material, and saves costs. However, it still has the following problems: Still adopting the three-section design concept in the prior art, resulting in a long liquid evaporation path and a complex device structure.

[0005] Serious liquid droplet entrainment: relying on a single vapor-liquid separation device to separate liquid droplets, without combining spatial distribution optimization, the humidity of the outlet steam is still as high as 1.2%; Limited thermal efficiency: the power density of each section of heat exchange tubes is the same, unable to adapt to the differential heat requirements of evaporation and superheating, and with high energy consumption; Structural redundancy: The multi-section partition plates and the support structure are complex, the shell-side pressure loss still reaches 10 kPa, and the maintenance cost is high. Summary of the Invention

[0006] In view of the above technical problems, the purpose of the present invention is to provide an integrated evaporation and superheating heat exchanger, which reduces structural redundancy through optimized design, reduces the steam evaporation pressure loss, improves the evaporation efficiency, and reduces the steam humidity.

[0007] In order to solve the above technical problems, the technical solution adopted by the present invention is as follows: On the one hand, the present invention provides an integrated evaporation and superheating heat exchanger, including: A shell, horizontally arranged; A partition plate, installed in the shell, dividing it into upper and lower space parts. The lower space part is an evaporation chamber, and the upper space part is a superheating chamber. And the evaporation chamber is smaller than the superheating chamber. A number of evaporation holes for steam to pass through are distributed on the partition plate; A first heating component, arranged in the evaporation chamber of the shell, for heating a liquid medium to generate steam; A second heating component, arranged in the superheating chamber of the shell, for heating the generated steam into superheated steam; A liquid inlet, arranged at the bottom of the shell, communicating with the evaporation chamber; and A steam outlet, arranged at the upper part of the shell, communicating with the superheating chamber, and the steam outlet and the liquid inlet are located at the same end of the shell.

[0008] Further, both the first heating component and the second heating component are heating tubes, and the heating tubes are fixed at the end of the shell through tube sheets.

[0009] Further, no evaporation holes are provided on the partition plate between the liquid inlet and the steam outlet facing each other.

[0010] Further, along the direction away from the liquid inlet, the aperture and the opening ratio of the evaporation holes both increase.

[0011] Further, the aperture and the opening ratio of the evaporation holes are distributed in a gradually changing manner or in a segmented manner.

[0012] Further, an arc-shaped baffle is arranged in the evaporation chamber.

[0013] Further, a spiral baffle is arranged in the superheating chamber.

[0014] Further, the heating tube is a U-shaped electric heating tube, the two ends of the U-shaped electric heating tube are fixed on the tube sheet, and the heating power of the U-shaped electric heating tube is distributed in a gradient manner, and the heating power of the section close to the liquid inlet is greater than that of the section far from the liquid inlet.

[0015] Further, a flow guiding cone angle is provided for the evaporation holes.

[0016] On the other hand, the present invention provides a method for generating superheated steam, which uses the above-mentioned integrated evaporation and superheating heat exchanger, and includes the following steps: Introduce water into the evaporation chamber through the liquid inlet; Start the first heating component and the second heating component; The first heating component heats the water in the evaporation chamber to generate steam; The steam enters the superheating chamber through the evaporation holes, and is heated into superheated steam by the second heating component and then output through the steam outlet.

[0017] Compared with the prior art, the beneficial effects of the present invention are as follows: The present invention has a small floor area and a compact structure. There is no need to separately set a preheating section. The present invention can meet the requirements without a baffle plate, and the pressure loss during the steam evaporation process is small. The present invention creatively uses a partition plate as a gas-liquid separator, eliminating the need for a separate gas-liquid separator. This makes the evaporation efficiency of the present invention high and the quality of the generated steam good. Description of the Drawings

[0018] Figure 1 It is a schematic diagram of the overall structure of the integrated evaporation and superheating heat exchanger of the present invention.

[0019] Figure 2 It is a longitudinal sectional view of the integrated evaporation and superheating heat exchanger of the present invention.

[0020] Figure 3 It is a partial sectional view of the integrated evaporation and superheating heat exchanger of the present invention.

[0021] Figure 4 It is a schematic diagram of the installation of the partition plate in the shell.

[0022] Figure 5 It is a schematic diagram of the evaporation holes on the partition plate of the present invention.

[0023] Figure 6 It is a schematic diagram of the installation of an arc baffle plate and a spiral baffle plate in the shell of the present invention.

[0024] Figure 7 It is a schematic diagram of the overall structure of the integrated evaporation and superheating heat exchanger of the present invention after removing the shell.

[0025] 1 - Shell, 2 - Liquid inlet, 3 - Steam outlet, 4 - End plate, 5 - Tube sheet, 6 - End cover, 7 - Partition plate, 8 - First heating component, 9 - Second heating component, 10 - Arc baffle plate, 11 - Spiral baffle plate; 810 - Heating tube, 110 - Superheating chamber, 120 - Evaporation chamber, 121 - Preheating section, 122 - Evaporation section, 123 - Final evaporation section, 710 - Evaporation holes, 701 - Holeless section, 702 - Small sparse hole section, 703 - Medium dense hole section, 704 - Large dense hole section. Detailed implementation mode

[0026] The following further describes the implementation mode of the present invention in detail in conjunction with the drawings and embodiments. The following embodiments are used to illustrate the present invention, but cannot be used to limit the scope of the present invention.

[0027] In the description of the present invention, it should be noted that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to the present invention. In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0028] In the description of the present invention, it should be noted that unless otherwise clearly specified and limited, the terms "connected" and "connected" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0029] As Figure 1 shown, the present invention provides an integrated evaporation and superheating heat exchanger, including: A housing 1, horizontally arranged; A partition 7, installed in the housing 1, dividing it into upper and lower space parts. The lower space part is an evaporation chamber 120, and the upper space part is a superheating chamber 110. And the evaporation chamber 120 is smaller than the superheating chamber 110. A number of evaporation holes 710 for steam to pass through are distributed on the partition 7; A first heating component 8, arranged in the evaporation chamber 120 of the housing 1, for heating a liquid medium to generate steam; A second heating component 9, arranged in the superheating chamber 110 of the housing 1, for heating the generated steam into superheated steam; A liquid inlet 2, arranged at the bottom of the housing 1, communicating with the evaporation chamber 120; and A steam outlet 3, arranged at the upper part of the housing 1, communicating with the superheating chamber 110, and the steam outlet 3 and the liquid inlet 2 are located at the same end of the housing 1.

[0030] The present invention uses a partition plate 7 to divide the housing 1 into upper and lower space portions, and evaporation holes 710 are provided on the partition plate 7 to isolate the water medium and steam, preventing excessive liquid water from being carried by the steam during evaporation; then, the second heating component 9 is used to heat the steam entering the superheat chamber 110 into superheated steam, further reducing the liquid water content carried by the steam to obtain high-quality superheated steam; compared with the prior art, the present invention creatively locates the steam outlet 3 and the liquid inlet 2 at the same end of the housing 1, eliminating the preheating section 121. When the liquid medium enters the evaporation chamber 120, its temperature is not high, so only a small amount of steam is generated. The water vapor carried by this part of the steam is less. Therefore, after entering the evaporation space through the evaporation holes 710 (part of the liquid water is blocked), it is very easy to heat it into superheated steam, resulting in a very low liquid water carry-over rate. The water temperature far from the liquid inlet 2 is higher, and the steam generation process is more intense, capable of generating a large amount of steam. At the same time, this part of the steam also carries a large amount of water. After being blocked by the partition plate 7 for a part, it enters the superheat chamber 110. Since it is already far from the steam outlet 3 at this time, there is enough residence time to be heated into superheated steam by the second heating component 9, greatly reducing the liquid water carry-over amount in the steam. Therefore, the present invention can, while maximizing the heating power of the first heating component 8 to increase the heat load of the entire heat exchanger, also ensure the superheat degree of the steam at the steam outlet 3. Through the spatial position design in cooperation with the isolation effect of the partition plate 7, the present invention eliminates the conventional preheating section, integrates the preheating section and the evaporation section, has a compact structure, occupies a small space, and can achieve a good evaporation effect without using a baffle plate. Therefore, the present invention has a high application value.

[0031] Exemplarily, such as Figure 1 , Figure 2 and Figure 7 shown, both the first heating component 8 and the second heating component 9 are heating tubes 810. The housing 1 is generally a circular tube structure. To facilitate the installation of the heating tubes 810, one end of the housing 1 is a closed end, which can be directly made into an integrated structure, or can be closed by an end plate 4. Of course, it can also be closed by a hemispherical end plate; the other end is an open end. The heating tubes 810 are fixed to the open end of the housing 1 through a tube sheet 5. Specifically, the heating tubes 810 are fixed to the tube sheet 5 by technical means such as welding or glue sealing, and then the tube sheet 5 is fixed to the end of the housing 1 through a detachable structure such as bolts.

[0032] Exemplarily, the heating tube 810 can be a hollow pipe through which a heating medium flows and is heated by the heating medium, or it can be an electric heating tube, and the specific type is not limited. Such as Figure 2 shown, Figure 2A end cover 6 is provided at the left end of the middle shell 1. Flange holes are provided at both ends of the shell 1. The end cover 6 and the tube sheet 5 are fixed on the flange holes at the left end of the shell together. The end cover 4 is fixed on the flange holes at the right end of the shell 1 to achieve detachable assembly. The end cover 6 has a certain accommodation space. When the heating tube 810 is an electric heating tube type, this accommodation space can accommodate a heating cable. When the heating tube 810 is a hollow pipeline, this accommodation space can accommodate a medium pipeline.

[0033] It should be noted that according to the spatial layout of the present invention, as Figure 2 , 3 , as shown in Figure 4, the evaporation chamber 120 can be divided into a multi-section structure. The section near the liquid inlet 2 is the preheating section 121, where almost no steam is generated or only a small amount of steam is generated. The partition plate 7 between the liquid inlet 2 and the steam outlet 3 facing each other is not provided with evaporation holes 710. The middle part is the evaporation section 122, where a medium amount of steam is generated, and the generated steam carries less liquid water. It is very easy to be reheated and evaporated into superheated steam after being heated by the second heating component 9. The section far from the liquid inlet 2 is the end evaporation section 123, where a large amount of steam is generated by intense evaporation, and at the same time, the steam also carries a large amount of liquid water. The entire evaporation chamber 120 is isolated by the partition plate 7 to prevent a large amount of liquid medium from violently fluctuating and entering the superheat chamber 110 during the evaporation process, thereby increasing the amount of liquid water carried by the steam. After the steam generated in each section enters the superheat chamber 110 through the evaporation holes 710, through the filtering action of the evaporation holes 710 and the pore wall tension action, part of the liquid water remains around the pore wall, gathers and then drops, realizing the preliminary separation of liquid water. The separated water vapor becomes superheated steam under the heating action of the second heating component 9 to reduce the steam humidity. According to the heating characteristics in the evaporation chamber 120, the fluid resistance is further reduced, and the steam humidity at the steam outlet 3 is reduced. Along the direction away from the liquid inlet 2, the aperture and the opening ratio of the evaporation holes 710 both increase. A small number of evaporation holes 710 with small apertures and medium apertures can meet the evaporation requirements of the evaporation section 122, and the evaporation holes 710 with large apertures and high opening ratios can meet the requirements of the end evaporation section 123. Since the end evaporation section 123 is the farthest from the steam outlet 3 and has the longest path, it has enough residence time to be heated into superheated steam by the second heating component 9 to reduce the humidity. The present invention creatively isolates the evaporation chamber 120 and the superheat chamber 110 by the partition plate 7 provided with evaporation holes 710, which not only avoids excessive liquid water carried by the steam caused by the disturbance generated by the evaporation and flow of the liquid, but also reduces the flow resistance of the steam and improves the energy conversion efficiency.

[0034] Exemplarily, the aperture and the opening ratio of the evaporation holes 710 are distributed in a gradient manner. The gradient distribution can ensure the minimum liquid water carrying amount at the maximum evaporation speed, which conforms to the temperature distribution trend of the liquid entering the evaporation chamber 120. However, the processing cost of the evaporation holes 710 on the partition plate 7 is high.

[0035] Exemplarily, the aperture diameter and the opening ratio of the evaporation holes 710 are distributed in a segmented manner. For example, a three-segment distribution (plus the non-opening area is four segments) can also meet the requirement of retrieving the liquid water carry-over while increasing the evaporation rate, and at the same time has a lower processing cost, which is the most economically feasible way.

[0036] See Figure 3 and Figure 4 , Figure 3 Figure 7 shows a schematic diagram of the partition plate 7 with a multi-segment distribution of the evaporation holes 710. From left to right, according to the aperture diameter and the distribution density of the evaporation holes 710, the partition plate 7 is arranged in 4 segments, which are the non-hole segment 701, the small and sparse hole segment 702, the medium and dense hole segment 703, and the large and dense hole segment 704 in sequence. Correspondingly, as Figure 4 shown, the evaporation chamber 120 below (separated by a dashed line) is the preheating section 121, the evaporation section 122, and the final evaporation section 123 in sequence; among them, the non-hole segment 701 is located between the liquid inlet 2 and the steam outlet 3. The evaporation of steam in the preheating section 121 is extremely small, but it is directly opposite to the liquid inlet 2, forming a temperature gradient. Therefore, the preheating section 121 covers the non-hole segment 701 and part of the small and sparse hole segment 702; in order to prevent the liquid medium in the liquid inlet 2 from causing turbulence during the turning process and directly entering the steam outlet 3, no evaporation holes 710 are provided on the partition plate 7 at the liquid inlet 2. In the evaporation section 122, the liquid temperature rises in a gradient manner, and the evaporation amount gradually increases. Therefore, it covers part of the small and sparse hole segment 702 and the medium and dense hole segment 703. Some of the evaporation holes 710 have a small density and a small aperture diameter, which can not only meet the evaporation requirements but also will not cause excessive liquid water entrainment. The small and sparse hole segment 702 on the left can ensure the quality of the superheated steam at the steam outlet 3; in the evaporation section 122, the liquid medium (such as water) is evaporated in large quantities. Therefore, evaporation holes 710 with a medium aperture diameter and a dense distribution are required to meet the evaporation demand. The medium and dense hole segment 703 is relatively far from the steam outlet 3, and the steam has enough travel distance to be heated by the second heating component 9 during the process of reaching the steam outlet 3 to evaporate the liquid water carried in the steam and obtain high-quality superheated steam; since the final evaporation section 123 is the farthest from the steam outlet 3, the steam has enough travel distance to be heated to the superheated state. Therefore, evaporation holes 710 with a large aperture diameter and a high density can be used to reduce the steam flow resistance; at the same time, when increasing the upper limit of the steam generation amount of the heat exchanger, the heating power of the first heating component 8 in the final evaporation section 123 can be greatly increased without affecting the quality of the superheated steam at the steam outlet 3, so as to obtain the maximum efficiency of superheated steam generation in a limited space, that is, the overall heating power of the heat exchanger can be improved.

[0037] Exemplarily, as Figure 3 shown, the design of the evaporation holes 710 on the partition plate 7 of the present invention is as follows: Small and sparse hole segment 702: aperture diameter 10 - 15 mm, hole pitch ≥ 150 mm, opening ratio 10% - 15%; Medium-dense hole section 703: pore diameter 15 - 20 mm, hole pitch 80 - 100 mm, hole opening rate 20% - 30%; Large-dense hole section 704: pore diameter 20 - 30 mm, hole pitch ≤ 50 mm, hole opening rate 40% - 50%.

[0038] The hole opening rate of the small-rare hole section 702 on the partition plate 7 is not greater than 15%, and the hole opening rate of the large-dense hole section 704 is not less than 40%. The forced steam rises concentratedly in the second half of the evaporation chamber 120, extending the flow path of the steam in the superheat chamber 110 (the path length increases by 1.5 - 2 times), and improving the superheat stability by increasing the entropy value.

[0039] Preferably, the hole shape of the evaporation holes 710 can be circular, long strip slit or Venturi contraction type. The Venturi holes with a 15° diversion cone angle at the edge are preferably adopted, as Figure 5 shown, which can not only reduce the resistance but also perform gas-liquid separation well.

[0040] Preferably, the partition plate 7 is made of shape memory alloy (such as Ni-Ti alloy). When the temperature exceeds 150 °C, the through-hole expansion rate can reach 8% - 12%, dynamically matching the change of steam flow rate.

[0041] Preferably, the small space of the evaporation chamber 120 (the height of the evaporation chamber ≤ 20% of the shell diameter) forces the steam to rise at a high speed (flow rate ≥ 2 m / s), and the liquid droplets fall back after hitting the bottom of the partition plate 7 due to inertia; the large space of the superheat chamber 110 (height ≥ 35% of the shell diameter) reduces the steam flow rate to 0.5 - 1 m / s, and further separates the liquid droplets by combining gravity sedimentation.

[0042] The present invention also has a secondary evaporation effect. The surface temperature of the heat exchange tubes in the superheat chamber 110 is higher than the steam saturation temperature, and the attached liquid droplets are secondarily evaporated when contacting the tube wall, reducing the outlet steam humidity to ≤ 0.5%.

[0043] Preferably, the heating power of the first heating assembly 8 is greater than that of the second heating assembly 9. For example, the lower evaporation chamber 120 adopts a high-power density design (8 - 12 kW / m²), enabling the liquid phase to complete the transition from nucleate boiling to film boiling within a short residence time (≤ 30 s) to avoid local dry-out; the power density of the upper superheat chamber 110 is reduced to 3 - 5 kW / m², and the "slow superheat" of the steam is achieved by reducing the heat flux density to avoid tube wall scaling caused by too rapid temperature rise.

[0044] The heating tube 810 is a U-shaped tube. The two ends of the U-shaped tube are fixed on the tube sheet 5. High-temperature heat transfer oil (300 - 400 °C) can flow inside the U-shaped tube, or it can be set as a U-shaped electric heating tube 810. The heating power of the U-shaped electric heating tube 810 adopts a gradient distribution, and the heating power of the section near the liquid inlet 2 is greater than that of the section far from the liquid inlet 2.

[0045] Preferably, as Figure 6 shown, a bow-shaped baffle 10 is provided in the evaporation chamber 120. The notch height of the bow-shaped baffle 10 is 20%-25% of the diameter of the housing 1. A flow guide grid (grid width 10-15 mm, Figure 6 not shown in the figure) is provided at the notch; the baffle spacing is 0.8-1.2 times the diameter of the housing 1, inducing the fluid to form a Dean vortex, and the heat transfer coefficient is increased by 15%-20%.

[0046] Preferably, as Figure 6 shown, a spiral baffle 11 is provided in the superheat chamber 110, forcing the steam to rise concentratedly in the second half of the superheat chamber 110, and extending the spiral flow path of the steam in the superheat chamber 110.

[0047] The present invention can be further optimized. The evaporation chamber 120 and the superheat chamber 110 are respectively divided into 3 independent temperature zones. Since the temperature of the incoming liquid is relatively low, the preheating section 121 requires high-power heating to quickly increase the temperature. In the evaporation section 122, the liquid temperature is already relatively high, so medium power can already maintain the heat required for evaporation. In the final evaporation section 123, since the liquid temperature is already very high, in order to prevent the liquid from boiling violently, the heating power can be reduced. Exemplarily, the present invention provides a power density (finally needs to be converted into the power of the heating tube) design as follows: Evaporation chamber 120: Preheating section 121 (0-20% length): power density 12-15 kW / m², preheating and temperature rising, quickly starting evaporation; Evaporation section 122 (20-80% length): power density 8-10 kW / m²; Final evaporation section 123 (80-100% length): power density 5-6 kW / m², preventing the outlet dryness from being too low.

[0048] The present invention divides the superheat chamber 110 into a preheating section, a main heating section, and a balancing section from right to left. In the preheating section of the superheat chamber, a relatively medium power is selected to increase the temperature of the steam. In the main heating section of the superheat chamber, a relatively high power is used to quickly increase the temperature of the steam to generate superheat; in the balancing section of the superheat chamber, which is close to the steam outlet 3, a relatively small power is used to maintain the superheated state of the steam. The specific power distribution is as follows: Preheating section of the superheat chamber: power density 3-4 kW / m²; Main heating section of the superheat chamber: power density 4-5 kW / m²; Balancing section of the superheat chamber: power density 2-3 kW / m².

[0049] In some embodiments, a capacitive liquid level gauge (accuracy ±1 mm) and a differential pressure transmitter (range 0 - 10 kPa) may be provided in the evaporation chamber 120; by monitoring the liquid level in the evaporation chamber 120, it is possible to prevent the liquid from overflowing upward through the partition plate 7; by monitoring the pressure in the evaporation chamber 120, the evaporation rate and whether the evaporation holes 710 are blocked can be determined.

[0050] In some embodiments, 5 - 7 groups of armored thermocouples (spacing 1 - 1.5 m) are arranged along the superheat chamber 110 to monitor the axial temperature gradient, and the superheat state of the steam in the superheat chamber 110 is judged by combining the pressure monitoring.

[0051] The present invention also provides a superheat chamber control strategy: when the detected dryness of the outlet steam of the evaporation chamber 120 < 98%, the power density of the main heat section of the superheat chamber is automatically increased to 7 - 8 kW / m².

[0052] Embodiment 2: The present invention provides a method for generating superheated steam, including the following steps: Water is introduced into the evaporation chamber 120 through the liquid inlet 2; The first heating component 8 and the second heating component 9 are started; The first heating component 8 heats the water in the evaporation chamber 120 to generate steam; The steam enters the superheat chamber 110 through the evaporation holes 710, and after being heated into superheated steam by the second heating component 9, it is output through the steam outlet 3.

[0053] Under the condition that the occupied volumes are roughly the same, the performance comparison between the present invention and CN111912260A (referred to as the prior art) is shown in Table 1. It can be seen that the evaporation rate of the present invention is fast and the energy consumption is low.

[0054] Table 1: Performance comparison table of the present invention

[0055] As can be seen from Table 1, the present invention has obvious technical advantages.

[0056] The above embodiments are only used to illustrate the present invention, rather than to limit the present invention. Although the present invention has been described in detail with reference to the embodiments, those of ordinary skill in the art should understand that various combinations, modifications or equivalent replacements of the technical solutions of the present invention do not depart from the spirit and scope of the technical solutions of the present invention, and should all be covered within the scope of the claims of the present invention.

Claims

1. An evaporation and superheating integrated heat exchanger, characterized in that: include: Shell, horizontal arrangement; A partition is installed in the shell to divide it into two spaces, the lower space is an evaporation chamber, and the upper space is an overheating chamber, and the evaporation chamber is smaller than the overheating chamber. The partition is provided with a plurality of evaporation holes for steam to pass through; A first heating component is disposed in the evaporation chamber of the shell and is used to heat the liquid medium to generate steam; A second heating assembly is disposed in the superheating chamber of the shell and is used to heat the generated steam into superheated steam; A liquid inlet is disposed at the bottom of the shell and communicates with the evaporation chamber; and The steam outlet is arranged at the upper part of the shell and is communicated with the superheating chamber, and the steam outlet and the liquid inlet are located at the same end of the shell.

2. The evaporation-superheating integrated heat exchanger according to claim 1, characterized in that: The first heating assembly and the second heating assembly are both heating tubes, and the heating tubes are fixed to the end of the shell through a tube plate.

3. The evaporation-superheating integrated heat exchanger according to claim 2, characterized in that: The partition between the liquid inlet and the steam outlet is not provided with an evaporation hole.

4. The evaporation-superheating integrated heat exchanger according to claim 2, characterized in that: Along the direction away from the liquid inlet, the pore size and the opening porosity of the evaporation hole both increase.

5. The evaporation and superheating integrated heat exchanger according to claim 4, characterized in that: The aperture and opening ratio of the evaporation holes are distributed in a gradual manner or in a segmented manner.

6. The evaporation and superheating integrated heat exchanger according to claim 2, characterized in that: An arcuate baffle is arranged in the evaporation chamber.

7. The evaporation and superheating integrated heat exchanger according to claim 2, characterized in that: A spiral baffle is arranged in the superheating chamber.

8. The evaporation-superheating integrated heat exchanger according to claim 2, characterized in that: The heating tube is a U-shaped electric heating tube, both ends of which are fixed on the tube plate. The heating power of the U-shaped electric heating tube is distributed in a gradient manner, and the heating power of a section close to the liquid inlet is greater than that of a section far from the liquid inlet.

9. The evaporation-superheating integrated heat exchanger according to claim 2, characterized in that: The evaporation hole is provided with a flow guide cone angle.

10. A method for generating superheated steam, using the evaporation-superheating integrated heat exchanger according to any one of claims 1 to 9, characterized in that: The following steps are involved: Introduce water into the evaporation chamber through the liquid inlet; Activate the first heating component and the second heating component; The first heating component heats the water in the evaporation chamber to generate steam; The steam enters the superheating chamber through the evaporation hole, is heated by the second heating component to become superheated steam, and is output through the steam outlet.

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