CN107664444B - Side-process plate and shell heat exchanger plates and multi-process removable plate and shell heat exchangers - Google Patents
Side-process plate and shell heat exchanger plates and multi-process removable plate and shell heat exchangers Download PDFInfo
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- CN107664444B CN107664444B CN201610607928.5A CN201610607928A CN107664444B CN 107664444 B CN107664444 B CN 107664444B CN 201610607928 A CN201610607928 A CN 201610607928A CN 107664444 B CN107664444 B CN 107664444B
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- 238000009826 distribution Methods 0.000 claims description 23
- 238000012546 transfer Methods 0.000 claims description 12
- 230000008859 change Effects 0.000 claims description 9
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/24—Arrangements for promoting turbulent flow of heat-exchange media, e.g. by plates
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- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention discloses a side-flow plate-shell type heat exchange plate and a multi-flow detachable plate-shell type heat exchanger. The heat exchanger plate has two transverse partitions and two communicating transverse flows or flow zones separated from each other are formed in the plate-side flow channels of the heat exchanger plate by means of plate-side baffle bars. By using the heat exchange plate, a more efficient single-flow plate heat exchanger can be built, and a multi-flow plate shell type heat exchanger with the plate side connecting pipes arranged on the front end flange cover and the heat exchange core body detachable can be built. The multi-flow plate-shell type heat exchanger is convenient to open and maintain and carry out mechanical cleaning.
Description
Technical Field
The invention relates to a plate-shell type heat exchanger, in particular to a side-flow plate-shell type heat exchange plate with transverse partitions and a multi-flow detachable plate-shell type heat exchanger using the same.
Background
The shell-and-tube heat exchanger (STHE), the Plate Heat Exchanger (PHE) and the plate-and-shell heat exchanger (PSHE) are all heat exchanger types well known to those skilled in the art, wherein the shell-and-tube heat exchanger is a dividing wall type heat exchanger in which the wall surface of a tube bundle enclosed in a shell is used as a heat exchange surface, the shell is mostly cylindrical, the tube bundle is installed inside the shell, two ends of the tube bundle are fixed on a tube plate, two kinds of cold and hot fluids for heat exchange respectively flow in a tube pass and a shell pass, and flow in a cross flow manner on the whole, and the heat exchanger has a simple structure and is reliable in operation; the plate heat exchanger is a high-efficiency heat exchanger formed by stacking a series of corrugated metal plates, a plurality of heat exchange plates are assembled together to form mutually alternate cold and hot flow channels, cold and hot fluid exchanges heat through the plates, the flow of the cold and hot fluid is parallel to a heat exchange surface and mostly adopts a parallel flow or countercurrent flow mode, and the heat exchanger has the characteristics of high heat exchange efficiency, small heat loss, compact and light structure, small floor area, convenience in installation and cleaning, long service life and the like.
The plate-shell type heat exchanger can be regarded as a structural form between the above-mentioned plate-shell type heat exchanger and plate type heat exchanger, and it can compromise the advantages of both: firstly, the plate is used as a heat transfer surface, so that the heat transfer efficiency is good; the cold and hot medium channels are alternatively arranged in the heat exchanger, the generated turbulence and complete countercurrent mode ensure extremely high heat transfer performance between the plates, and the heat transfer coefficient can be several times higher than that of a shell-and-tube heat exchanger. Secondly, the structure is compact and the volume is small. And thirdly, the heat resistance and the compression resistance are realized, the highest working temperature can reach 800 ℃, the highest working pressure can reach 6.3 MPa, and the special form can also be applied to higher temperature and pressure. The corrugated plate surface causes higher surface shear stress and is not easy to scale. Fifthly, the plate-shell heat exchanger with the special end cover flange structure can be disassembled to clean the heat exchange channel. The plate-shell type heat exchanger is particularly suitable for the process occasions with large difference of the heat exchange medium flow on two sides, the shell side channel allows large flow to pass through due to the flexibility of the configuration connecting pipe, and the small flow heat exchange medium enters the plate side channel of the heat exchanger. As described above, the plate-and-shell type heat exchanger becomes a high-performance heat exchange device widely used in various industrial fields due to the combination of the advantages of the plate-and-shell type heat exchanger. The popularity of such heat exchangers is attributed to its many unique and advantageous product attributes, including high heat transfer coefficient, all-welded construction, no or minimal gasket material, suitability for high temperature, high pressure, low temperature, low pressure conditions, and high flexibility to be accurately custom-selected for operating conditions.
Fig. 1A is a schematic structural diagram of an operating principle of a plate-shell heat exchanger as a prior art, and as shown in fig. 1A, a typical plate-shell heat exchanger mainly includes: the heat exchanger comprises connecting pipes Ai and Ao for a plate side fluid (A fluid) to enter and exit the heat exchanger, connecting pipes Bi and Bo for a shell side fluid (B fluid) to enter and exit the heat exchanger, a heat exchanger shell C and a heat exchange core body D positioned in the heat exchanger shell C, wherein the heat exchange core body D consists of a series of sequentially assembled cold-pressed round heat exchange plates. Furthermore, as shown in the physical diagram of the heat exchange plate on the right side of fig. 1A, each heat exchange plate is further provided with two round holes F as an inlet and an outlet for the plate-side fluid, two adjacent heat exchange plates are tightly welded together along the peripheral contact position to form a plate pair E, the plate pair E forms a flow channel for the plate-side fluid, the two plate pairs E are welded together along the periphery of the round holes F to form a flow channel for the shell-side fluid, and the completely welded cylindrical heat exchange core D is finally installed in the heat exchanger shell C, so that a shell-side flow space is formed. The details of the construction of the round heat exchanger plates for a conventional plate and shell heat exchanger are shown more clearly in fig. 1B, where round inlets 5 and round outlets 6 for the plate side fluid are provided at the upper and lower ends of the heat exchanger plates of a conventional plate and shell heat exchanger, respectively, and different forms of corrugations 2 formed by cold pressing are provided at the surface of the heat exchanger plates to enhance the flow turbulence and heat transfer coefficient, as shown in fig. 1B. As mentioned above, the two heat exchanger plates are welded together along the periphery 3 to form a plate pair E as shown in fig. 1A, with fluid a flowing inside the plate pair (i.e. forming a plate side flow channel); the adjacent plate pairs E are welded together along the circular hole edges of the circular inlet and outlet 5, 6 to seal the plate-side flow channels and the shell-side flow channels, and the fluid B flows between the plate pairs in the shell (i.e. the shell-side flow channels are formed).
Although not shown in the above schematic drawings, front and rear end caps are also provided at the front and rear ends of the shell-and-plate heat exchanger shell, respectively, which are welded together with the heat exchanger shell to form pressure-bearing and sealing capabilities. If the heat exchanger shell is required to have the capacity of being opened to clean the heat exchange channel, the front end cover can be designed to be of a flange structure, and the front end cover and the heat exchange core body are welded together and connected together through the flange connecting pipe between the front end cover and the heat exchanger shell. When the heat exchange channel needs to be cleaned, the front end cover and the heat exchange core body can be integrally drawn out of the shell. In addition, enough clearance must be provided between the heat exchange core and the shell to ensure the distribution of the shell side fluid in the axial direction, and in order to make almost all the shell side fluid flow through the heat exchange core, a flow guide mechanism must be installed between the heat exchange core and the inner wall of the shell, so that the flow short circuit between the heat exchange core and the shell is reduced to the greatest extent. For a technical solution specially for solving the problem of the diversion sealing, see US 8453721B 2.
The same as the rectangular heat exchange plates of the plate heat exchanger, the circular heat exchange plates forming the heat exchange core of the plate-shell heat exchanger greatly affect the overall performance and working condition of the heat exchanger, and generally speaking, the performance of the plate-shell heat exchanger can be adjusted and optimized through the change of the following parameters: 1) the heat exchange plate is provided with plate lines; 2) heat exchanger plate size (diameter); 3) plate hole size and center hole spacing; 4) the number of plates; and 5) the number of flows of the cold and hot fluids. It should be noted that the flow path and the flow channel in the technical field belong to technical terms related to each other but having different meanings, and taking a plate heat exchanger as an example, the flow path refers to a group of parallel flow channels in the plate heat exchanger in which one medium flows in the same direction, and the flow channel refers to a medium flow channel formed by two adjacent plates in the plate heat exchanger. While the same concept exists in plate-and-shell heat exchangers, the flow path and flow channel are further defined as plate side and shell side, taking into account their structural considerations. According to the above definitions, fig. 1A shows that the plate-shell heat exchanger is designed as a single-pass or single-shell-pass.
Theoretically, the requirement of any high efficiency working condition can be met by increasing the change of the flow number under the condition that other parameters are kept unchanged, and particularly, a multiple pass design (multiple passes design) is sometimes required for industrial application with low flow rate or small temperature difference. Fig. 2 shows a schematic diagram of a three-flow plate-shell heat exchanger, which is composed of a shell 10, a heat exchange core 11, a front end cover 18 and a rear end cover 19. Cold fluid (shell side fluid, a fluid) 17 enters the heat exchanger from the connection pipe 12 at the lower end of the shell side, flows upward in the first flow, flows downward in the second flow, flows upward again in the third flow, and then flows out of the heat exchanger from the connection pipe 13 at the upper end of the shell side. The hot fluid (plate side fluid, B fluid) 16 flows in from the connection pipe 14 at the rear end cover 19, and similarly flows through three flow paths and flows out of the heat exchanger from the connection pipe 15 at the front end cover 18. As shown, the cold and hot fluids flow in opposite directions in each flow path to form counter-flow to maximize the heat exchange potential.
Despite the numerous advantages, the conventional plate and shell heat exchangers still suffer from a series of technical problems and inconveniences in use as follows:
1) as shown in fig. 1B, due to the inherent geometric features of the round heat exchange plates, the length and width of the flow channel of the plate-side fluid of the plate-shell heat exchanger are relatively low, about 1.0, compared with the rectangular heat exchange plates of the plate heat exchanger. Therefore, for industrial application with small temperature difference, the design of the single-flow heat exchange plate cannot effectively transfer heat, thermal optimization cannot be often achieved, and the heat exchange area required by the same working condition is higher than that of a detachable plate heat exchanger, so that the cost of the heat exchanger is obviously increased.
2) Also due to the inherent geometry of the circular heat exchanger plates, the flow of plate side fluid between the inlet and outlet ports is inherently non-uniform. The fluid flow path 7 near the central region is shortest and the flow velocity is greatest; the fluid flow path 8 is longest and the flow velocity is smallest near the peripheral region, and this flow non-uniformity affects the overall heat exchange performance. International application WO 2012159882 a1 discloses attempts to reduce this non-uniformity to some extent by introducing baffle corrugations between the inlet and outlet, but this does not fundamentally address the inherent weakness of the short flow path of the circular heat exchanger plates described in 1).
3) For applications with higher heat exchange efficiency requirements, the only practical solution to the short flow path is to use a multi-flow design. In the prior art, a method for realizing a multi-flow plate-shell heat exchanger is to divide a heat exchange core into a plurality of groups. Between each two sub-groups, baffles or deflectors are installed, forcing the plate-side fluid to change direction of flow. And a baffle or a flow baffle plate is also required to be arranged at a corresponding position on the shell side so as to ensure that the flow on the plate side and the shell side is kept in a counter-flow state. However, as shown in fig. 2, the multi-flow design of the plate-and-shell heat exchanger always requires the installation of the connection pipe 14 on the rear end cover 19, but for pressure-bearing and sealing reasons, the plate-side connection pipe must be welded to both the heat exchange core 11 and the rear end cover 19 to achieve complete sealing between the heat exchange core 11 and the shell 10. In this case, the front and rear end covers of the multi-flow plate-shell heat exchanger must be welded to the shell, so that the multi-flow plate-shell heat exchanger cannot be opened for mechanical cleaning, but only for chemical cleaning. For this reason, multi-pass plate and shell heat exchangers are generally only suitable for industrial applications where the fluids on both sides are clean.
Disclosure of Invention
The object of the present invention is to solve the above-mentioned technical problems of the prior art, and in particular to solve the two main drawbacks of the plate and shell heat exchanger described above: 1) the single plate flow is too short, so the whole heat exchange capacity is reduced; 2) the plate-shell heat exchanger under the multi-flow design can not be opened, so that mechanical cleaning can not be carried out.
According to a first aspect of the present invention, there is provided a side flow heat exchange plate for a plate and shell heat exchanger, the side flow heat exchange plate defining two lateral zones in its plate side flow passages by means of plate side baffle bars, wherein the length of the plate side baffle bars is less than the radial length of the heat exchange plate to allow a plate side fluid to flow between the two lateral zones communicating at one end, and wherein the plate side fluid inlet and outlet circular holes are respectively provided on both sides of the other end of the two lateral zones which are not communicating.
Preferably, in the side-flow heat exchange plate according to the first technical aspect, the side-flow heat exchange plate forms two lateral partitions in the shell-side flow channel thereof by means of shell-side baffle bars, wherein the length of the shell-side baffle bars is equal to the radial length of the heat exchange plate, so as to realize shell-side baffle of the shell-side fluid in a state of countercurrent flow to the plate-side fluid.
According to a second aspect of the present invention, there is provided a quarantined heat exchange plate for a plate-and-shell heat exchanger, said quarantined heat exchange plate forming two lateral partitions in its plate-side flow channels by means of plate-side baffle bars, wherein the length of said plate-side baffle bars is equal to the radial length of the heat exchange plate, thereby forming two mutually isolated lateral partitions in said plate-side flow channels, and a pair of round inlet and outlet holes for said plate-side fluid are respectively provided at the upper and lower ends of said two mutually isolated lateral partitions.
Preferably, in the heat exchange plate of the isolation zone according to the second technical solution, the heat exchange plate of the isolation zone forms two transverse partitions in the shell-side flow channel thereof by means of shell-side baffle bars, wherein the length of the shell-side baffle bars is equal to the radial length of the heat exchange plate, so as to realize shell-side baffle of the shell-side fluid in a countercurrent state with the plate-side fluid.
Preferably, in the above technical solution, the heat exchange plate is circular or elliptical.
Preferably, in the above technical solution, the heat exchange plates may obtain different thermal performances by changing geometric characteristics, and the heat exchange plates with different geometric characteristics may be mixedly disposed in the same heat exchange core.
Preferably, in the above technical solution, the geometrical features include smooth surfaces, V-shaped fish ripples, round or irregular pits, spikes, and other structures for enhancing heat exchange.
According to a third technical scheme of the invention, a plate-shell type heat exchanger is provided, which comprises a front end cover, a rear end cover, a shell and a heat exchange core body, wherein a plurality of side-flow heat exchange plates according to the first technical scheme are welded together along the periphery and round inlet and outlet holes alternately to form the heat exchange core body with plate-side flow channels and shell-side flow channels alternating with each other.
According to a fourth technical scheme of the invention, a multi-flow plate-shell heat exchanger is provided, which comprises a front end cover, a rear end cover, a shell and a heat exchange core body, wherein a plurality of side-flow heat exchange plates according to the first technical scheme are welded together along the periphery and the round inlet and outlet holes alternately to form two flow heat exchange core body parts close to the rear end cover, and a plurality of isolation region heat exchange plates according to the second technical scheme are welded together along the periphery and the round inlet and outlet holes alternately to form all other flow heat exchange core body parts except the two flow heat exchange plates close to the rear end cover.
Preferably, in the multi-flow plate-and-shell heat exchanger according to the above technical solution, the side-flow heat exchange plates are used for completing the flow direction turning in the longitudinal direction, so that no plate-side connection pipe needs to be arranged on the rear end cover, and the heat exchange core body can be detached from the shell.
Preferably, in the plate-and-shell heat exchanger according to the above technical solution, the plate-side flow channels and the shell-side flow channels are formed by planar contact between adjacent heat exchange plates, and the shell-side flow guiding, baffling and isolating mechanisms do not require welding.
Preferably, in the plate and shell heat exchanger according to the above-described solution, the shell-side flow guiding, baffling and isolating mechanism may be partially or completely replaced by a welded structure or other sealing structure.
Preferably, in the plate-shell heat exchanger according to the above technical solution, through the effective arrangement of the baffle bars and the shell-side baffle plates on the heat exchange plates, the relative flow direction between adjacent heat exchange flow channels can be set to be a completely reverse flow, a completely cocurrent flow, a mixed flow in a reverse cocurrent direction, or a cross flow, so as to achieve thermal optimization under different application conditions.
According to the technical scheme of the invention, the structure and design of the novel heat exchange plate for the plate-shell type heat exchanger are disclosed, and the multi-process plate-shell type heat exchanger which is higher in heat exchange efficiency and easy to maintain/clean because the plate-side connecting pipes are arranged on the front-end flange cover is realized. The features, technical effects and other advantages of the present invention will become apparent from the following further description when taken in conjunction with the accompanying drawings.
Drawings
The invention will now be described, by way of example, with reference to the accompanying drawings, in which:
fig. 1A is a partially exploded schematic view showing the working principle of a conventional single-pass plate-and-shell heat exchanger, and also shows a physical view of a circular heat exchange plate used in the conventional plate-and-shell heat exchanger;
FIG. 1B shows a detail of the construction of a circular heat exchanger plate for a conventional plate and shell heat exchanger;
FIG. 2 is a schematic diagram of the working principle and flow of a conventional three-flow plate-shell heat exchanger;
fig. 3 is a schematic diagram of the structure and operation of a side flow heat exchange plate with transverse zoning, exemplified by a flow path of a plate-side fluid, according to an embodiment of the invention;
FIG. 4 is a schematic diagram of the structure and operation of a side flow heat exchange plate with transverse zoning, exemplified by the flow path of the shell side fluid, according to an embodiment of the invention;
FIG. 5 is a simplified assembly and flow diagram of a plate and shell heat exchanger employing side flow heat exchange plates according to an embodiment of the present invention;
FIG. 6 is a schematic view of the structure and operation of an exclusion zone heat exchanger plate with transverse exclusion zones, as exemplified by the flow path of the plate-side fluid, according to a variation of the present invention;
FIG. 7 is a schematic illustration of the structure and operation of an insulated zone heat exchanger plate with transverse insulated partitions, exemplifying flow paths for shell side fluids, according to a variant of the present invention;
fig. 8 is a simplified assembly and flow diagram of a multi-pass plate and shell heat exchanger with a removable heat exchange core according to a variant of the invention.
Detailed Description
The technical contents and constructional features of preferred embodiments of the invention, as well as the technical objects and technical effects achieved, are explained in detail below with reference to the accompanying drawings.
First, the present invention overcomes the following technical limitations regarding round heat exchanger plates of conventional plate and shell heat exchangers: taking the plate-side flow as an example, the plate-side fluid flows unidirectionally on the circular heat exchange plate, the plate-side flow on a single heat exchange plate is relatively short, and the flow of the plate-side fluid between the inlet and the outlet of the circular heat exchange plate is uneven, which affects the overall heat exchange capability. Secondly, the invention also overcomes the following technical prejudices regarding conventional multi-flow plate-shell heat exchangers: the multi-flow plate-shell type heat exchanger needs to be provided with a plate-side fluid interface and a connecting pipe thereof at a front end cover and a rear end cover respectively, and the front end cover and the rear end cover of the plate-shell type heat exchanger are welded with a heat exchanger shell, so that the plate-shell type heat exchanger cannot be opened for mechanical cleaning and only can be chemically cleaned. The above technical limitations and prejudices are largely present in the prior art documents describing plate and shell heat exchangers, which the inventors have radically overcome by means of an inventive solution, the core inventive idea being to divide a conventional circular heat exchanger plate into two transverse partitions and to form two flow partitions at the plate side and the shell side, which are connected to each other or isolated from each other, by means of a special zebra design, the details of construction and the working principle being described below.
In conventional single pass plate and shell heat exchangers, where the plate-side flow is too short, thus reducing the overall heat exchange capacity, according to a preferred embodiment of the present invention, the key component that helps to solve this problem is a circular heat exchange plate with two Lateral partitions and with the inlet and outlet circular holes for the plate-side fluid arranged to the same end, this special heat exchange plate may be referred to as a side-flow heat exchange plate (specific plate), the detailed working principle of which is explained in conjunction with fig. 3-5.
Fig. 3 is a schematic diagram of the working principle of a side flow heat exchanger plate with transverse partitions, exemplified by the flow path of the plate-side fluid, according to an embodiment of the invention; FIG. 4 is a schematic diagram of the operation of a side flow heat exchange plate with transverse zoning, exemplified by the flow path of the shell side fluid, according to an embodiment of the invention; fig. 5 is a simplified assembly and flow diagram of a single pass plate and shell heat exchanger employing side-pass heat exchange plates according to an embodiment of the present invention. The intermediate plate-side baffle strips 22 shown in fig. 3 are formed by two flat ridges pressed on two adjacent round heat exchanger plates in contact with each other, so that the pressure between the assembled plates of the heat exchanger core ensures the required sealing without welding. Also shown in fig. 3 is the flow trajectory of the plate side fluid having two communicating laterally zoned side flow heat exchange plates, first the plate side fluid flows in via the lower right inlet round hole 20, the intermediate plate side baffle bars 22 prevent the plate side fluid from flowing directly to the lower left outlet round hole 21 and guide the plate side fluid to flow in the direction indicated by arrow 23 via the plate internal flow channels to the top of the heat exchange plates. Secondly, since the length of the plate-side baffle bars 22 is smaller than the diameter of the circular heat exchanger plate, an opening 24 is left in the top of the heat exchanger plate to allow the plate-side fluid to flow laterally from the right-hand sub-section to the left-hand sub-section. Then, the plate-side fluid is guided in the direction indicated by the arrow 25 to further flow downward via the in-plate flow channels, and finally flows out from the outlet circular hole 21 at the lower left. The transverse flow path design doubles the flow distance on the same circular heat exchange plate, and reduces the flow channel width and the flow cross-sectional area by about one time, so that the length-width ratio of the flow channel on the circular plate with the same diameter is increased from about 1 to about 4, the flow speed and the heat exchange coefficient under the same flow rate are obviously improved, and the heat exchange capacity under the small temperature difference is also obviously improved. At the same time, the flow non-uniformity of the plate side fluid is significantly improved over the conventional circular heat exchanger plate shown in fig. 1B.
In a plate and shell heat exchanger, the flow path for the shell-side fluid is formed by two adjacent plate pairs, and the intermediate shell-side baffle 28 shown in fig. 4 is formed by two straight lines protruding toward the shell side, which are in contact with each other, on two directly opposite heat exchange plates of the two adjacent plate pairs. Also shown in fig. 4 is the flow trajectory of the shell-side fluid of a side-flow heat exchanger plate with two lateral partitions, it being noted that the position of the shell-side inlet and outlet connections 12, 13 on the heat exchanger shell is adjusted accordingly and that, unlike the plate-side baffle bars 22, the shell-side baffle bars 28 extend over the entire plate diameter. First, shell side fluid flows into the heat exchanger from shell side inlet connection 12 and enters gap distribution area 30 between shell 10 and heat exchange core 11, one side of distribution area 30 is sealed by guide plate 31, and the other side is blocked by bottom baffle plate 29. Thus, the shell side fluid flows upward through the interplate flow channels in the direction indicated by arrow 32 and into the top distribution zone 33. The shell side fluid then flows from the left hand partition to the right hand partition and further down through the interplate flow channels in the direction indicated by arrow 34. Finally, the shell-side fluid enters gap distribution 35 between shell 10 and heat exchange core 11 and exits the heat exchanger from shell-side outlet connection 13 under the combined restriction of right-side flow guide 31 and bottom baffle 29. Because the flow areas of the shell-side fluid and the plate-side fluid are approximately the same, but the flow directions are exactly opposite, a high degree of pure countercurrent flow can be formed, and the maximum heat transfer potential is realized.
In fig. 5 a complete single pass plate and shell heat exchanger is shown using the side-pass heat exchanger plates shown in fig. 3 and 4. As shown in fig. 5, the single-pass plate-and-shell heat exchanger according to the embodiment of the present invention comprises a shell 10, a front end cover 18, a rear end cover 19, and a heat exchange core assembled by a series of side-pass heat exchange plates 56 according to the embodiment of the present invention, wherein a baffle 29 is located at the bottom of the heat exchange core. The plate-side fluid enters the heat exchanger through inlet connection 14 provided on front end cover 18 and exits the heat exchanger through outlet connection 15 provided on front end cover 18, while the shell-side fluid flows into the heat exchanger through shell-side connection 12 and exits the heat exchanger through outlet connection 13. This arrangement shown in figure 5 is substantially equivalent to a plate side double pass heat exchanger but no nipples are provided on the rear end cap 19.
It should be particularly noted that the side-flow heat exchange plates described above can also be configured in any number of flow paths of the multi-flow plate and shell heat exchanger using the conventional design shown in fig. 2, and the side-flow heat exchange plates of the embodiment of the present invention can be configured to increase the thermal flow length by a factor of two, in other words, the flow path of the plate-side fluid by a factor of two, and the aspect ratio of the flow path by a factor of about 3, compared to the multi-flow plate and shell heat exchanger using the same number of flow paths of the conventional heat exchange plates shown in fig. 1B. In addition, the plate pass design according to the embodiment of the invention can be used in combination with the conventional shell pass design, and is not limited to the case that the plate pass design according to fig. 3 and the shell pass design according to fig. 4 must be adopted at the same time, which is similar to the case that multiple tube passes and multiple shell passes can be used in combination in a shell-and-tube heat exchanger, and the modification cost of the conventional shell-and-plate heat exchanger can be saved to a certain extent. In summary, the side-flow heat exchange plate according to the embodiment of the present invention ideally solves the problems caused by the short plate-side flow and the non-uniformity of the flow of the plate-side fluid in the conventional plate-shell heat exchanger.
Furthermore, the above-mentioned side-flow heat exchange plate according to the embodiment of the present invention may be further extended to another important flow layout modification, so that the multi-flow plate-shell heat exchanger manufactured according to the configuration of the modification of the present invention does not need to have any connecting pipe on the rear end cover, and therefore the heat exchange core of the multi-flow plate-shell heat exchanger may also be extracted from the shell for mechanical cleaning, which fundamentally overcomes the technical bias in the prior art, and the detailed working principle of the modification is explained in conjunction with fig. 6 to 8.
FIG. 6 is a schematic diagram of the operating principle of an insulated zone heat exchanger plate with transverse insulated partitions, exemplified by the flow path of the plate-side fluid, according to a variant of the invention; FIG. 7 is a schematic diagram of the operating principle of an insulated zone heat exchanger plate with transverse insulated partitions, exemplified by the flow path of the shell side fluid, according to a variant of the invention; fig. 8 is a simplified assembly and flow diagram of a multi-pass plate and shell heat exchanger with a removable heat exchange core according to a variant of the invention. Fig. 6 shows the structural design and working principle of a circular heat exchanger plate according to a variant, the heat exchanger plate shown in fig. 6 differs from the side flow heat exchanger plate shown in fig. 3 in two places: 1) the length of the baffle strips on the plate side is increased to the whole diameter, and the plate surface is divided into a left isolation area and a right isolation area; 2) in each side isolation area, a pair of round holes for inlet and outlet of plate-side fluid are respectively arranged at the upper end and the lower end, and this special variant heat exchange plate can be called as an isolation area heat exchange plate, or simply called as an isolation area plate (Isolated partial plate).
Specifically, the plate-side baffle strips 28 and 61 shown in fig. 6 are formed by two straight lines pressed on two adjacent round heat exchange plates, which are in contact with each other, so that welding is not required, and the pressure between the assembled back plates of the heat exchange core body can ensure the required sealing. It should be noted that the two plate side flow strips 28, 61 serve to isolate the plate side flows in different flow paths and thus may be considered as a central plate side baffle strip as a whole. Also shown in fig. 6 are the flow trajectories of the plate side fluid in the left and right two lateral isolation zones of the exclusion zone heat exchanger plate, in the right isolation zone the plate side fluid flows in via the inlet round hole 20 and directly to the corresponding outlet round hole 64 and into the next pass, and in the left isolation zone the plate side fluid from the previous pass flows in the opposite direction via the inlet round hole 63 and directly to the corresponding outlet round hole 21.
As described above, in the shell-and-plate heat exchanger, the flow path of the shell-side fluid is formed by two adjacent plate pairs, and the two shell-side baffle bars 28, 61 shown in fig. 7 are formed by two straight ridges protruding toward the shell side on two directly opposite heat exchange plates in the two adjacent plate pairs contacting each other. It should be noted that the two shell-side baffle strips, which extend over the entire diameter of the disk as well as their plate-side baffle strips, can also be considered as a central shell-side baffle strip as a whole. The flow trajectories of the shell-side fluid in the left and right two transverse separation zones using such an isolation zone heat exchanger plate are also shown in fig. 7, and in the left separation zone, the shell-side fluid flowing into the heat exchanger from the shell-side inlet connection 12 enters the gap distribution zone 30 between the shell 10 and the heat exchange core 11, and one side of the distribution zone 30 is sealed by a guide plate 31, and the other side is blocked by a bottom baffle plate 29. Thus, the shell side fluid flows upward through the interplate flow channels in the direction indicated by arrow 32 and into the top distribution zone 33. Since the right side of the top distribution area 33 is blocked by the top baffle 67, the shell side fluid can only flow axially/longitudinally to the next pass. In the right isolation zone, the shell-side fluid from the previous pass flows down through the plate-to-plate flow channels in the direction indicated by arrow 34 under the combined restriction of top baffle 67 and right baffle 31, then enters gap distribution region 35 between shell 10 and heat exchange core 11, and finally exits the heat exchanger through shell-side outlet connection 13 under the combined restriction of right baffle 31 and bottom baffle 29. Likewise, because the flow areas of the shell-side fluid and the plate-side fluid are approximately the same, but the flow directions are exactly opposite, a high degree of pure counterflow conditions can be established, achieving maximum heat transfer potential. In addition, through the effective arrangement of the baffle strips on the heat exchange plates and the baffle plates at the shell side, the relative flow direction between the adjacent heat exchange flow channels can be set to be completely reverse flow, completely cocurrent flow, reverse cocurrent mixed flow or cross flow, so that the thermodynamic optimization under different application working conditions is realized.
It should be noted that the flow directions of the plate-side fluid and the shell-side fluid in a specific flow path are shown in fig. 6 and 7, while the flow directions of the cooling fluid in the adjacent flow paths are changed, and it is not difficult for those skilled in the art to understand that the flow directions of the plate-side fluid and the shell-side fluid are changed, and therefore, the description will be omitted here. In addition, the plate pass design according to the modified example of the present invention can also be used in combination with the conventional shell pass design, and is not limited to the case that the plate pass design according to fig. 7 and the shell pass design according to fig. 7 must be adopted at the same time, which can save the modification cost of the conventional plate-shell heat exchanger to a certain extent.
By using the heat exchange plates in the side-flow heat exchange plate isolation area in combination, a higher flow number (such as 4, 6, 8, 10 and any even flow number) meeting the working condition requirements can be realized, and it should be noted that, because each heat exchange plate has two flows, if each heat exchange plate is taken as a reference, the achievable flow number can be practically any value, and the limitation of even flow is avoided), and the plate side connecting pipes are all arranged on the multi-flow plate shell type heat exchanger of the detachable heat exchange core body on the front end cover. In the plate-shell type heat exchanger with high flow number, two flows close to one side of the rear end cover use the side flow heat exchange plate, and the rest other flows use the isolation area heat exchange plate. In fact, the function of the middle-side flow heat exchange plate in the multi-flow design is to make the cold and hot fluid turn around by 180 degrees before reaching the rear end cover, so as to avoid any plate-side connection pipe on the rear end cover.
Fig. 8 shows the structure and flow principle of a six-flow plate-and-shell heat exchanger according to a variant of the present invention, which, as shown in fig. 8, comprises a front end cover 18, a rear end cover 19, and a heat exchange core assembled from a set of side-flow heat exchange plates 56 and two sets of isolation zone heat exchange plates 65, wherein a bottom baffle 29 and a top baffle 67 are respectively located at the bottom and the top of the heat exchange core. The plate-side fluid enters the heat exchanger through inlet connection 14 provided on front end cover 18 and exits the heat exchanger through outlet connection 15 provided on front end cover 18, while the shell-side fluid flows into the heat exchanger through shell-side connection 12 and exits the heat exchanger through outlet connection 13. The working process of the six-flow detachable plate-shell heat exchanger is described by taking a complete flow path of a plate-side fluid as an example, the plate-side fluid enters the heat exchanger from an inlet connecting pipe 14 on a front end cover 18, a first flow path and a second flow path are completed in different isolation area heat exchange plates, wherein the first flow path flows upwards, and the second flow path flows downwards; then, a third flow and a fourth flow are completed on the same side of the heat exchange plate, wherein the third flow flows upwards, and the fourth flow flows downwards; finally, a fifth flow path and a sixth flow path are completed in the heat exchange plates of the isolation area corresponding to the first flow path and the second flow path respectively, wherein the fifth flow path flows upwards, the sixth flow path flows downwards, and the fluid on the last plate side flows out of the heat exchanger from the outlet connecting pipe 14 on the front end cover 18. The flow path of the shell-side fluid is exactly related to the flow path of the plate-side fluid, and the operation process thereof will be easily understood by those skilled in the art with reference to fig. 7, and thus the description thereof will be omitted. As can be seen from fig. 8, the side flow heat exchanger plates are used only in the third and fourth passes next to the side of the rear end cover, and the isolation zone heat exchanger plates are used in the other passes, in this variant of the multi-pass design, the side flow heat exchanger plates are actually used to perform a pass direction Turn (U-Turn) in the longitudinal direction to allow the inlet and outlet connections for the plate side fluid to be all mounted to the front end cover, thus eliminating the need for any plate side connections on the side of the rear end cover.
Compared with the traditional design structure, the plate-shell type heat exchange plate designed according to the embodiment and the modification of the invention and the plate-shell type heat exchanger configured according to the plate-shell type heat exchange plate have the following advantages:
-the problem of short veneer flow of the round plate-shell type heat exchange plate is solved: the plate-shell type heat exchange plate designed according to the invention changes a circular flow channel into two transverse subareas through special baffle bars, thereby reducing the flow cross-sectional area, increasing the flow length of a plate-side flow path, and increasing the length-width ratio of the flow channel on the same diameter of the circular plate from about 1 to about 4.
-the detachability of the heat exchange core body of a multi-flow structure is realized: through mixing the use side flow heat exchange plate and the isolation region heat exchange plate, the detachability of the heat exchange core body of the multi-flow plate-shell type heat exchanger can be realized, and any plate side connecting pipe does not need to be arranged on the rear end cover. This configuration allows the shell side to be opened for mechanical cleaning, thereby allowing the multi-pass plate and shell heat exchanger to be used in industrial applications where fouling of one side is likely.
-overall more efficient heat exchangers: due to the advantages, the single-flow or multi-flow plate-shell heat exchanger with higher heat exchange efficiency, lower cost and easy maintenance can be designed and manufactured according to the invention, and the requirements of high-efficiency and maintainability plate-shell heat exchangers in high-temperature, high-pressure, low-temperature and low-pressure applications are met.
According to the working condition parameters and the required flow number, the plate-shell type heat exchange plate has the following two typical application examples. Both applications require two sets of ports and baffle bar shapes.
[ first application example ]
In the first application only side flow heat exchanger plates are used, which are suitable for any number of flow applications.
-pressing side flow heat exchanger plates according to embodiments of the invention.
And welding a plurality of side flow heat exchange plates together along the periphery and the circular holes of the inlet and the outlet alternately to form a heat exchange core body with alternate cold and hot flow channels. If the flow path is multi-flow path, a flow baffle plate with blind holes is needed to be used at the position of flow path change. The baffle plate and other heat exchange plates are from the same die, and the only difference is that one of the round holes is not flushed so as to change the flowing direction of the plate-side fluid.
For each pass, baffles are installed on the top or bottom of the heat exchange core. In the case of a single pass, only a baffle plate needs to be installed at the bottom.
Welding the heat exchange core, the front and rear end caps, the shell, the plate edge connecting tubes and the shell side connecting tubes together to form the integral heat exchanger.
If single pass, both nipples on the plate side are at the front end cap; if the multi-flow is adopted, one connecting pipe on the plate side is arranged on the front end cover, and the other connecting pipe on the plate side is arranged on the rear end cover.
[ second application example ]
In the second application example, the side flow heat exchange plates and the isolation area heat exchange plates are used in combination to realize a multi-flow plate-shell heat exchanger with a detachable heat exchange core (for example, 4, 6, 8, 10 and any even number of flows, if each heat exchange plate is taken as a reference, the achievable number of flows can be practically any value, and there is no limitation of an even number of flows).
-pressing two types of heat exchanger plates separately according to embodiments and variants of the invention. Wherein the first type is an isolation zone heat exchanger plate according to a variant of the invention and the second type is a side-flow heat exchanger plate according to an embodiment of the invention, which is only suitable for use in a flow against a back cover.
-alternately welding together a plurality of isolation zone heat exchanger plates along the periphery and circular holes to form part of the heat exchanger core in all other processes except the two processes adjacent to the rear end cover.
-alternately welding together a plurality of side flow heat exchange plates along the periphery and the circular holes to form a heat exchange core part of both flows adjacent to the rear end cover.
-welding the heat exchange core, the flange-type front end cover, the heat exchange core and the plate-side adapter together to form a core assembly.
-welding together the circular housing, the back pressure plate, the shell-side mating flange and the shell-side nipple to form a housing assembly.
-clamping the core assembly and the shell assembly together by means of a plurality of bolts arranged around the periphery of the flanges to complete the integral heat exchanger, with annular sealing gaskets provided between the flanges. In this multi-flow shell-and-plate heat exchanger, both connection pieces on the plate side are on the front end cover. And thus can be opened for mechanical cleaning.
In the above embodiments and modifications, the shell-side flow (shell pass) and the plate-side flow (plate pass) of the plate-and-shell heat exchanger according to the technical solution of the present invention have the same number and length but opposite directions, so that the pure countercurrent state of the plate-side fluid and the shell-side fluid is realized, and the heat exchange efficiency between the cold fluid and the hot fluid is improved to the maximum extent. However, it is particularly emphasized that the plate-side design according to the invention and the shell-side design according to the prior art can be used in conjunction in the plate-shell heat exchanger according to the invention, in other words, the plate-side flow can be modified only according to the solution of the invention depending on the particular industrial application, which has a certain cost advantage in particular in the modification of conventional plate-shell heat exchangers.
From the foregoing it will be appreciated that, although various embodiments of the invention have been described and illustrated, the invention is not limited thereto but may be otherwise embodied within the scope of the subject matter defined in the following claims. For example, for industrial applications (evaporator, condenser) where one side of the fluid undergoes a phase change, the fluid that does not undergo a phase change may be arranged on the plate side of the side-flow heat exchange plate described herein to increase the single-phase heat transfer coefficient, and the fluid that undergoes a phase change may be arranged on the shell side. However, no deflection is required on the shell side. This can achieve efficient design of local 1 flow versus 2 flow. Furthermore, for example, industrial applications (evaporators, condensers) where one or both sides of the fluid are phase-changed and where there is a need for superheating or subcooling, the phase-changed fluid may also be arranged on the plate side of the side-flow heat exchange plates described in the present invention. One side partition of the same heat exchange plate is used for evaporation or condensation, and the other side partition can be used for realizing overheating or supercooling, so that the efficient design of a local 1 process to a 2 process can be realized. Also, for example, the outer shell, the end plates and the heat exchanger plates may have an oval shape or the like. Such an elliptical shape is included in the term "circular" in the context of the present description. The heat exchanger may also have additional flow channels, and multiple end plates and housings may thus have more than one respective inlet and outlet ports.
The above disclosure is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the scope of the present invention, therefore, the present invention is not limited by the appended claims. It is to be understood that the above description is intended to be illustrative, and not restrictive. For example, the above-described embodiments (and/or aspects thereof) may be used in combination with each other. In addition, many modifications may be made to adapt a particular situation or material to the teachings of the invention without departing from its scope. Many other embodiments and modifications within the scope and spirit of the claims will be apparent to those of skill in the art from reading the foregoing description.
Claims (13)
1. A side flow heat exchange plate for a plate-shell heat exchanger is characterized in that: the side-flow heat exchange plate forms two transverse subareas in a plate-side flow passage thereof by means of plate-side baffle bars, and forms two transverse subareas in a shell-side flow passage thereof by means of shell-side baffle bars, wherein the length of the plate-side baffle bars is smaller than the radial length of the heat exchange plate so as to allow a plate-side fluid to flow between the two transverse subareas communicated at one end, and inlet and outlet circular holes for the plate-side fluid are respectively arranged at two sides of the other end, which is not communicated with the two transverse subareas, and wherein the length of the shell-side baffle bars is equal to the radial length of the heat exchange plate so as to realize shell-side baffle of the shell-side fluid and the plate-side.
2. The utility model provides an isolation zone heat transfer plate for lamella heat exchanger which characterized in that: the isolating area heat exchange plate forms two transverse subareas on a plate side flow passage of the isolating area heat exchange plate by means of plate side baffle bars, and forms two transverse subareas on a shell side flow passage of the isolating area heat exchange plate by means of shell side baffle bars, wherein the length of the plate side baffle bars is equal to the radial length of the heat exchange plate so as to form two mutually isolated transverse subareas on the plate side flow passage, a pair of round inlet and outlet holes for plate side fluid are respectively arranged at the upper end and the lower end of the two mutually isolated transverse subareas, and the length of the shell side baffle bars is equal to the radial length of the heat exchange plate so as to realize shell side baffle of the shell side fluid and the plate side fluid in a countercurrent state.
3. A heat exchanger plate according to claim 1 or 2, wherein: the heat exchange plate is circular or oval.
4. A heat exchanger plate as claimed in claim 3, wherein: the heat exchange plates can obtain different thermal performances through the change of geometric characteristics, and the heat exchange plates with different geometric characteristics can be mixedly arranged in the same heat exchange core.
5. A heat exchanger plate according to claim 4, wherein: the geometric features include smooth surfaces, V-shaped fish ripples, rounded or irregular dimples, spikes, and other structures for enhancing heat transfer.
6. A plate and shell heat exchanger comprising front and rear end caps, a shell and a heat exchange core, wherein a plurality of side-flow heat exchange plates as claimed in claim 1 are welded together along the periphery and round inlet and outlet holes alternately to form said heat exchange core with alternate plate-side and shell-side flow channels.
7. A plate and shell heat exchanger as claimed in claim 6, wherein: the shell side fluid enters a first gap distribution area between the shell and the heat exchange core body from a shell side inlet connecting pipe, one side of the first gap distribution area is sealed by a left side guide plate, the other side of the first gap distribution area is blocked by a bottom guide plate, the first gap distribution area flows upwards through the plate-to-plate flow channels and flows from a left side transverse partition area to a right side transverse partition area in a top distribution area, the second gap distribution area further flows downwards to enter a second gap distribution area between the shell and the heat exchange core body, and the second gap distribution area flows out from a shell side outlet connecting pipe under the limitation of the bottom guide plate.
8. A multi-pass plate and shell heat exchanger comprising front and rear end caps, a shell and a heat exchange core, wherein a plurality of side-pass heat exchange plates of claim 1 are welded together along the periphery and round inlet and outlet holes alternately to form two-pass heat exchange core portions abutting against the rear end cap, and a plurality of isolation region heat exchange plates of claim 2 are welded together along the periphery and round inlet and outlet holes alternately to form all other-pass heat exchange core portions except the two-pass heat exchange plates abutting against the rear end cap.
9. The multi-flow plate and shell heat exchanger of claim 8, wherein: the side flow heat exchange plate is used for completing flow direction turning in the longitudinal direction, so that a plate side connecting pipe is not required to be arranged on the rear end cover, and the heat exchange core body can be detached from the shell.
10. The multi-flow plate and shell heat exchanger of claim 8, wherein:
in the left isolation subarea of the heat exchange plate of the isolation area, shell side fluid enters a first gap distribution area between the shell and the heat exchange core body from a shell side inlet connecting pipe, wherein one side of the first gap distribution area is sealed by a left side guide plate, and the other side of the first gap distribution area is blocked by a bottom baffle plate, flows upwards through the flow channels between the plates, enters a top distribution area on the right side, and flows to the next flow path along the axial direction;
in the right side isolation subarea of the isolation area heat exchange plate, shell side fluid from a previous flow path flows downwards through the plate-to-plate flow channels under the common limitation of the top baffle plate and the right baffle plate, enters a second gap distribution area between the shell and the heat exchange core body, and flows out from a shell side outlet connecting pipe under the common limitation of the right baffle plate and the bottom baffle plate.
11. A plate and shell heat exchanger according to any one of claims 6 to 10, wherein: the plate-side and shell-side flow channels are formed by planar contact between adjacent heat exchange plates, and the shell-side flow guiding, baffling and isolating mechanisms do not need to be welded.
12. A plate and shell heat exchanger as claimed in claim 11, wherein: the shell-side flow directing, baffling and isolation mechanisms may be partially or completely replaced by welded structures or other sealing structures.
13. A plate and shell heat exchanger as claimed in claim 12, wherein: through the effective arrangement of the baffle strips on the heat exchange plates and the baffle plates at the shell side, the relative flow direction between the adjacent heat exchange flow channels can be set to be completely reverse flow, completely cocurrent flow, reverse cocurrent mixed flow or cross flow, so that the thermodynamic optimization under different application working conditions is realized.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610607928.5A CN107664444B (en) | 2016-07-28 | 2016-07-28 | Side-process plate and shell heat exchanger plates and multi-process removable plate and shell heat exchangers |
| PCT/CN2017/093801 WO2018019182A1 (en) | 2016-07-28 | 2017-07-21 | Side-flow plate and shell-type heat exchanging plate and multi-flow detachable plate and shell-type heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610607928.5A CN107664444B (en) | 2016-07-28 | 2016-07-28 | Side-process plate and shell heat exchanger plates and multi-process removable plate and shell heat exchangers |
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| Publication Number | Publication Date |
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| CN107664444A CN107664444A (en) | 2018-02-06 |
| CN107664444B true CN107664444B (en) | 2021-04-02 |
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| CN201610607928.5A Expired - Fee Related CN107664444B (en) | 2016-07-28 | 2016-07-28 | Side-process plate and shell heat exchanger plates and multi-process removable plate and shell heat exchangers |
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| Country | Link |
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| CN (1) | CN107664444B (en) |
| WO (1) | WO2018019182A1 (en) |
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| DK179767B1 (en) * | 2017-11-22 | 2019-05-14 | Danfoss A/S | Heat transfer plate for plate-and-shell heat exchanger and plate-and-shell heat exchanger with the same |
| CN109737775B (en) * | 2019-03-06 | 2024-04-12 | 山东恒辉节能技术集团有限公司 | Efficient and easy-to-clean sewage heat exchanger |
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| CN111442669A (en) * | 2020-05-20 | 2020-07-24 | 武汉联合立本能源科技有限公司 | Mining serial-type heat transfer system of decontaminating |
| CN112361852B (en) * | 2020-10-28 | 2022-07-26 | 武汉第二船舶设计研究所(中国船舶重工集团公司第七一九研究所) | Printed circuit board heat exchanger |
| CN114508956A (en) * | 2020-11-16 | 2022-05-17 | 丹佛斯有限公司 | Plate and shell heat exchanger and heat transfer plate for a plate and shell heat exchanger |
| CN114623630B (en) * | 2020-12-09 | 2024-07-09 | 广东美的白色家电技术创新中心有限公司 | Heat exchanger and dish washer |
| CN112284164B (en) * | 2020-12-10 | 2025-01-17 | 江苏金诺化工装备有限公司 | Large baffle rod type heat exchanger for petrochemical industry and use method thereof |
| CN112902730A (en) * | 2021-04-19 | 2021-06-04 | 高拓石油天然气技术（上海）有限责任公司 | Full-surface heat exchange plate, heat exchange core and heat exchanger |
| CN113883929B (en) * | 2021-09-28 | 2023-10-17 | 浙江搏克换热科技有限公司 | Heat exchange equipment of intelligent temperature monitoring |
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| CN102706188A (en) * | 2012-06-04 | 2012-10-03 | 哈尔滨工程大学 | High-pressure resistant lamella heat exchanger adopting round corrugated plates |
| CN103868394A (en) * | 2012-12-13 | 2014-06-18 | 杭州三花研究院有限公司 | Circulation board of heat exchanger, heat exchanging unit of heat exchanger and heat exchanger |
| CN205980877U (en) * | 2016-07-28 | 2017-02-22 | 恒丰工程（香港）有限公司 | Side flow plate-shell type heat exchange plate and multi-flow detachable plate-shell type heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2018019182A1 (en) | 2018-02-01 |
| CN107664444A (en) | 2018-02-06 |
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