CN104180693B - A new type of full countercurrent rotating non-mixing heat exchanger - Google Patents

Abstract

The present invention is that a kind of novel full adverse current rotates without direct contact heat exchanger; Except heat exchanger pedestal, heat exchanger other parts in use rotate, heat exchanger by heat exchanger cylindrical shell, flow channel converter, end socket in heat exchanger, heat exchanger outside head and heat exchanger pedestal are formed; The full adverse current realizing two fluids, without the rotary heat exchange of mixing, reaches the object strengthening heat transfer effect.Heat exchanger cylindrical shell is the cylindrical tube that there are more than 2 or 2 even number baffle plates an inside, cylindrical shell is evenly divided into multiple even number decile by baffle plate, left and right sides baffle plate and the cylindrical tube part folded by centre thereof form a fan-shaped runner, adopt flow channel converter as runner conversion equipment.This heat exchanger is used for fluid thermal and exchanges occasion, has heat exchange efficiency high, and heat exchange mean temperature difference is large, and the outlet temperature uniformity is high, without features such as mixing between heat exchanging fluid.Of the present invention of many uses, can be applicable to the heat conduction reinforced or temperature homogenisation in commercial Application between different fluid.

Description

A new type of full countercurrent rotating non-mixing heat exchanger

technical field

The invention relates to a novel full countercurrent rotating non-mixing heat exchanger, which belongs to the technical category of fluid heat exchange equipment.

Background technique

The heat transfer process is very common in industrial processes and daily life, and is one of the basic physical processes in nature. It is widely used in departments such as power, chemical industry, metallurgy, aerospace, air conditioning, refrigeration, machinery, textile, construction and so on. The heat transfer process is closely related to the cooling of microelectronic devices as large as a turbogenerator with a single unit power of 1.3 million kilowatts. Heat exchanger is a general-purpose equipment widely used in the heat transfer process. In oil refining enterprises, the equipment investment of heat exchanger accounts for about 25% of the total investment, and the weight of heat exchanger accounts for 20% of the total weight of equipment. Taking a power plant as an example, the investment in heat exchange equipment such as various boilers, condenser heaters, etc. accounts for about 70% of the investment in the entire power plant. In refrigeration equipment, the weight of evaporator and condenser also accounts for more than 30% of the weight of the whole unit.

Due to the importance of the heat exchanger in the actual application process, from the perspective of energy saving, in order to further reduce the volume of the heat exchanger, reduce the weight and metal consumption, reduce the power consumed by the heat exchanger, and enable the heat exchanger to Working under a lower temperature difference, various methods must be used to enhance the heat transfer in the heat exchanger. Therefore, how to enhance the heat transfer effect has been the main direction of heat transfer research in the past ten years. At present, the main means of enhancing heat transfer include the following: 1. Increase the heat transfer area, through fins, heterogeneous surfaces, porous material structures, and reduce pipe diameter; 2. Increase the average heat transfer temperature difference, through countercurrent or misalignment 3. Increase the total heat transfer coefficient, reduce the heat transfer boundary layer effect, increase the gas flow rate, enhance the gas disturbance, add solid particles to the fluid, and use short-tube heat exchangers.

At present, the heat exchangers used for heat transfer mainly include tube heat exchangers, plate heat exchangers, and heat pipe heat exchangers. The heat exchanger and its strengthening technology are mainly based on the improvement of the static structure. Finned tubes, threaded tubes, tube inserts and other technologies are used to increase the heat exchange area, strengthen the degree of turbulence, and reduce the heat transfer resistance. At present, there are relatively few studies on dynamic heat exchangers. CN103175420A discloses a core rotary heat exchanger, which mainly increases the turbulence of the shell-side fluid of the tube-and-tube heat exchanger by rotating the heat exchange core. To achieve the purpose of enhancing the heat transfer effect. CN202013125U discloses a fluid impingement rotary heat exchanger, which adopts the method of setting an impeller on the shell side of the shell-and-tube heat exchanger, relying on the shell side fluid to flow through the impeller rotation to increase the disturbance of the shell side, thereby achieving increased heat transfer purpose of the effect. The present invention adopts fan-shaped spaced flow channel design, and the hot and cold fluids are all rotated to increase the disturbance degree of the fluid, peel off the heat transfer boundary layer, and achieve the purpose of enhancing the heat transfer effect.

Contents of the invention

The purpose of the present invention is to provide a new type of fully mixed-flow rotary non-mixed heat exchanger, which is used in fluid heat exchange occasions, has high heat exchange efficiency, large average temperature difference of heat exchange, high uniformity of outlet temperature, and heat exchange fluid There is no mixing and so on.

The present invention is realized through the following technical scheme, a new type of fully mixed-flow rotary non-mixing heat exchanger, which is characterized in that the heat exchanger cylinder 7 is a cylindrical cylinder with multiple baffles inside, and the baffles divide the cylinder The body is evenly divided into several even-numbered equal parts, and the baffles on the left and right sides and the cylindrical body part sandwiched in the middle form a fan-shaped flow channel. The channel converters 5 and 6 are channel conversion devices with the same structure, and their basic components are the outer baffle plate 6-1 of the channel converter, the inner baffle plate 6-2 of the channel converter and the partition plate 6 of the channel converter -3, on the left side of the flow channel converter 6, the outer baffle plate 6-1 and the left edge of the inner baffle plate 6-2 form a circle, the inside of the circle is section E, and the outside of the circle is connected to the flow channel converter The annular part between the cylinders 7 is a section G, the area formed between the inner baffle 6-2 and the flow channel converter partitions 6-3 on both sides and the heat exchanger cylinder 7 is a section H, and the outer baffle Section F is the area formed between 6-1 and the flow channel converter partitions 6-3 on both sides. The right section of the outer baffle 6-1 is an arc shape, and the right arcs of all the outer baffles are concentric, and the right section of the outer baffle 6-1 coincides with the heat exchanger cylinder 7, and the flow The right side edge of the channel exchanger partition plate 6-3 coincides with the left side of the heat exchanger shell 7 baffle plate. All flow channel converter internal baffles 6-1 intersect at one point on the right side, which coincides with the left center point of the heat exchanger cylinder 7 baffles. The cross section on the left side of the channel converter 6 coincides with the cross section on the right side of the heat exchanger inner head 2 . The right side section of the heat exchanger outer head 1 coincides with the right side section of the heat exchanger cylinder. The flow channel converter 5, the heat exchanger outer head 3, and the heat exchanger inner head 4 are the flow channel converter 6, the heat exchanger outer head 1, and the heat exchanger inner head 2 respectively. Mirror image of the central section in the direction. Except for the heat exchanger base 8 and the heat exchanger base 9, all other components are axisymmetric structures along the left and right axial directions. The upper arc-shaped surfaces of the heat exchanger base 8 and the heat exchanger base 9 coincide with the outer surface of the heat exchanger cylinder. In the above structure, except for the heat exchanger base 8 and the heat exchanger base 9, all other components rotate at the same speed in the axial direction under the condition of external force during use.

The number of baffles in the above-mentioned heat exchanger can be 2 or more even numbers, and the number of baffles in the channel converter is the same, and the number of inner and outer baffles in the channel converter is half of the above number.

The ratio of the area of the left section E of the flow channel converter of the above heat exchanger to the area of the left section of the heat exchanger cylinder is 0.1-0.9:1

The taper of the inner baffle and the outer baffle of the flow channel converter of the heat exchanger is 10-170 degrees.

The sub-arc section of the A end face circle of the above-mentioned double-cone multi-channel mixing unit body, the ratio of the arc section used to form the convex edge of the vertebral surface and the arc section corresponding to the arc section used to form the vertebral surface groove is 0.5-2: 1

Except for the heat exchanger base 8 and the heat exchanger base 9 of the above structure, the speed of axial rotation of the remaining parts during use is 0-100r/s.

The principle of the novel fully counter-current rotating non-mixing heat exchanger described in the present invention is that the cold fluid flows in from the annular section A on the left side of the heat exchanger, and the fluid touches the inner head 2 of the heat exchanger. Due to being blocked on the left side surface, it flows into the G channel of the flow channel converter 6 along the left side surface of the inner head, and the liquid in the G channel is blocked by the outer baffle plate of the heat exchanger channel converter 6 and enters the flow channel. The H flow channel of the channel converter 6, while flowing through the flow channel corresponding to the H flow channel in the heat exchanger cylinder in the H flow channel, the fluid flows through the heat exchanger cylinder and enters the heat exchanger flow channel conversion The F flow channel of the device 5 is simultaneously subjected to the effect of the outer baffle plate of the heat exchanger flow channel converter 5, gathers toward the center, and enters the E flow channel of the heat exchanger flow channel converter 5. After the stream of fluid flows through the channel converter 5, due to the blocking effect of the left surface of the heat exchanger inner head 4, it gathers toward the center and finally flows out from the central fluid outlet section D on the right side of the heat exchanger. The hot fluid flows in from the annular section C on the right side of the heat exchanger. When the fluid touches the right side surface of the inner head 4 of the heat exchanger, due to being blocked, it flows into the G flow of the flow channel converter 5 along the left side surface of the inner head 4. The liquid in the G channel enters the H channel of the channel converter 5 due to the blocking effect of the outer baffle plate of the heat exchanger channel converter 5, and flows through the heat exchanger cylinder in the H channel and connects with the H channel at the same time. The flow channel corresponding to the flow channel, the fluid flows through the heat exchanger cylinder and enters the F flow channel of the heat exchanger channel converter 6, and is simultaneously affected by the outer baffle plate of the heat exchanger channel converter 6, Gather to the center and enter the E flow channel of the heat exchanger flow channel converter 6. After the fluid flows through the flow channel converter 6, due to the blocking effect of the right side surface of the heat exchanger inner head 2, the fluid gathers toward the center and finally flows out from the central fluid outlet section B on the left side of the heat exchanger. The hot and cold fluids exchange heat in the channels of the heat exchanger, and the channels are spaced apart from each other so that no mixing occurs. During the flow of hot and cold fluids in the heat exchanger, due to the influence of the rotation of the heat exchanger itself, when the fluid passes through the heat exchanger, its streamline is a spiral forward, which increases the flow of the fluid in the heat exchanger distance. At the same time, due to the existence of rotation, the degree of turbulence of the fluid is increased, and the boundary layer of heat exchange is updated. At the same time, due to the existence of rotation, the fluid is continuously self-mixed inside the flow channel, which increases the temperature uniformity of the fluid outlet and improves the efficiency. The average temperature difference of heat exchange achieves the purpose of enhancing heat transfer.

The invention has a wide range of uses and can be applied to heat transfer enhancement or temperature homogenization between different fluids in industrial applications. When applied to different occasions, different structural parameters can be selected.

As a novel heat exchanger, the present invention has the following advantages:

1. Simple structure, convenient manufacture and installation, due to the use of rotating structure, the weight of metal materials required to achieve the same flow pattern is reduced, thereby reducing equipment investment;

2. The full counter-flow heat exchange increases the average temperature difference of heat exchange and strengthens the heat transfer effect.

3. The heat transfer efficiency is high, the homogenization effect of the fluid temperature is obvious, and the residence time is well improved;

4. Low flow resistance, less energy consumption to achieve the same heat transfer effect;

5. Fully streamlined design, no dead zone in the flow, and there will be no situation where individual streams cannot flow out of the mixer;

6. The peeling effect on the boundary layer is better, the internal fluid continuously impacts the heat transfer surface, enhances the convective heat transfer coefficient in the tube, and strengthens the heat transfer;

7. The flow channels of the hot and cold fluids are always kept separated during the rotation process, and there is no mixing phenomenon;

8. According to different application occasions and operating conditions, the structural parameters of the unit body can be flexibly changed to achieve optimization.

Description of drawings

Figure 1 is a schematic diagram of the overall structure of the present invention.

FIG. 2 is a schematic structural diagram of the outer sealing head 1 and the outer sealing head 3 .

Fig. 3 is a structural schematic diagram of the inner head 2 and the inner head 4

Fig. 4 is a structural schematic diagram of the channel converter 5 and the channel converter 6

Fig. 5 is a structural schematic diagram of the heat exchanger cylinder 7

FIG. 6 is a structural schematic diagram of the heat exchanger base 8 and the heat exchanger base 9 .

In the figure, 1 is the outer head on the left side of the heat exchanger, 2 is the inner head on the left side of the heat exchanger, 3 is the outer head on the right side of the heat exchanger, 4 is the inner head on the right side of the heat exchanger, and 5 is the heat exchanger The right channel converter of the heat exchanger, 6 is the left channel converter of the heat exchanger, 6-1 is the outer baffle of the channel converter, 6-2 is the inner baffle of the channel converter, 6-3 7 is the shell of the heat exchanger, 8 is the right side base of the heat exchanger, and 9 is the left side base of the heat exchanger. A is the circular fluid inlet section on the left side of the heat exchanger, B is the circular fluid outlet section on the left side of the heat exchanger, C is the annular fluid inlet section on the right side of the heat exchanger, D is the circular outlet section on the right side of the heat exchanger, E is the left central cross-section of the flow channel converter, F is the cross-section between two flow channel converter partitions and a flow channel converter outer baffle, G is the left side of the flow channel converter and the heat exchanger cylinder The annular cross section formed by the body, H the cross section between two flow channel converter partitions, a flow channel converter inner baffle and the heat exchanger cylinder.

detailed description

The following is an embodiment of the present invention in terms of heat transfer enhancement, but the role of the full counter-current rotary non-mixed heat exchanger is not limited to this, and it is only an example for illustration.

Example

The main body length of the fully countercurrent rotating non-mixed heat exchanger is 1m, and the diameter is 0.4m. The number of plates and each flow channel converter partition is 8, and the number of each flow channel converter outer baffle and inner baffle is 4. The thickness of the original is 1mm and the material is stainless steel. The cross-sectional diameter on the left side of the flow channel converter is 0.3m. The experimental medium is air, the flow rate of cold air is 11.3 cubic meters per second, the inlet temperature is 300K, the flow rate of hot air is 11.3 cubic meters per second, and the inlet temperature is 800K. Fluent fluid dynamics calculation software is used for simulated heat transfer calculations. The obtained heat transfer effect was compared with that of the shell and tube heat exchanger under the same heat transfer area. The shell and tube heat exchanger has a shell diameter of 0.4m, a core length of 1m, and a tube diameter of 0.05m. For comparison under the same total heat transfer area: the heat transfer power of the full countercurrent rotary non-mixing heat exchanger is 924W, the total heat transfer coefficient is 4.55W/m ² K, and the temperature unevenness of the cold fluid outlet is 22K. The heat transfer power of the ordinary shell and tube heat exchanger is 530W, the total heat transfer coefficient is 1.17W/m ² K, and the temperature unevenness of the cold fluid outlet is 67K. It can be seen from the results that under the same conditions, compared with the ordinary shell-and-tube heat exchanger, the heat transfer power of the new full-counter-current rotary non-mixing heat exchanger is increased by 74%, and the total heat transfer coefficient is increased by 289%. The unevenness of the outlet temperature has also been significantly reduced.

Claims (10)

1. novel full adverse current rotates without a direct contact heat exchanger, it is characterized in that, except heat exchanger pedestal, heat exchanger other parts in use rotate, heat exchanger is by heat exchanger cylindrical shell, flow channel converter, end socket in heat exchanger, heat exchanger outside head and heat exchanger pedestal are formed; The full adverse current realizing two fluids, without the rotary heat exchange of mixing, reaches the object strengthening heat transfer effect.

2. heat exchanger as claimed in claim 1, it is characterized in that heat exchanger cylindrical shell is the cylindrical tube that there are more than 2 or 2 even number baffle plates an inside, cylindrical shell is evenly divided into multiple even number decile by baffle plate, left and right sides baffle plate and the cylindrical tube part folded by centre thereof form a fan-shaped runner, adopt flow channel converter as runner conversion equipment.

3. heat exchanger as claimed in claim 1, it is characterized in that described flow channel converter, be made up of multiple interior outer baffle and dividing plate, the quantity of flow channel converter dividing plate is identical with the quantity of heat exchanger inner barrel baffle plate, the quantity of interior outer baffle is respectively the half of above-mentioned quantity, H passage and the F channel spacing of flow channel converter arrange, and are connected respectively with the sector channel of heat exchanger cylindrical shell.

4. heat exchanger as claimed in claim 1, is characterized in that described interior end socket entrance section and flow channel converter E cross section coincide.

5. heat exchanger as claimed in claim 1, is characterized in that described outside head outlet and heat exchanger cylindrical shell cylindrical cross-section coincide.

6. heat exchanger as claimed in claim 1, is characterized in that described heat exchanger pedestal top circular cross-section and heat exchanging body cylindrical shell cross section coincide.

7. heat exchanger as claimed in claim 1, is characterized in that the area of the left side cross-sectional E of the flow channel converter of heat exchanger and the ratio of heat exchanger cylindrical shell left side cross-sectional area are 0.1-0.9:1.

8. heat exchanger as claimed in claim 1, is characterized in that the Internal baffle of the flow channel converter of heat exchanger and the tapering of outer baffle are 10-170 degree.

9. heat exchanger as claimed in claim 1, is characterized in that point segmental arc of the A end face circle of the flow channel converter of heat exchanger, is 0.5-2:1 for the segmental arc forming vertebra face fin with the ratio of the corresponding central angle of segmental arc for forming vertebra face groove.

10. heat exchanger as claimed in claim 1, it is characterized in that heat exchanger is overall except pedestal (9) on the left of pedestal on the right side of heat exchanger (8) and heat exchanger, the speed that remainder in use rotates vertically is 0-100r/s.