Spiral plate heat exchanger

Abstract

A first channel and a second channel which are adjacent and spirally arranged from outside to inside are arranged in the spiral plate heat exchanger, the first channel and the second channel are both vertically arranged, the center of the top of the first channel is open and communicated with a cold medium outlet connecting pipe at the top of the heat exchanger, and the periphery of the top of the first channel is closed. An outer port of the first channel is communicated with a cold medium inlet connecting pipe at the side part of the heat exchanger; the center of the bottom of the second channel is open and communicates with a first heat medium connecting pipe at the bottom of the heat exchanger, and an outer port of the second channel communicates with a second heat medium connecting pipe on the side of the heat exchanger. The upper portion of the first channel is provided with a gas phase channel which extends from outside to inside and is communicated with the first channel, and an inner port of the gas phase channel is communicated with an opening in the center of the top of the first channel. Compared with the prior art, the steam resistance can be reduced.

Description

Technical Field

[0001] The utility model belongs to the technical field of heat exchangers, and particularly relates to a spiral plate heat exchanger. Background Art

[0002] Existing spiral plate heat exchangers such as the structures disclosed in the Chinese utility model patent No. 202121863007.8 "A multi-stream spiral plate heat exchanger" (authorization announcement No. CN215984131U) and the Chinese utility model patent No. 202120801664.3 "A spiral plate heat exchanger with a sealing structure" (authorization announcement No. CN215373649U).

[0003] In the case where the medium produces a gas phase during the heat exchange process (such as steam generated when water is heated), the spiral channel inside the spiral plate heat exchanger makes it impossible for the gas phase medium to be discharged in time, resulting in vapor resistance. Utility Model Content

[0004] The technical problem to be solved by the utility model is to provide a spiral plate heat exchanger capable of reducing steam resistance in view of the current status of the existing technology.

[0005] The technical solution adopted by the present invention to solve the above technical problems is as follows: a spiral plate heat exchanger having a first channel and a second channel adjacent to each other and arranged spirally from the outside to the inside, the first channel and the second channel being arranged vertically, and the top central portion of the first channel being open and connected to the cold medium outlet pipe at the top of the heat exchanger, the top peripheral portion of the first channel being closed, and the outer port of the first channel being connected to the cold medium inlet pipe at the side of the heat exchanger; the bottom central portion of the second channel being open and connected to the hot medium pipe 1 at the bottom of the heat exchanger, and the outer port of the second channel being connected to the hot medium pipe 2 at the side of the heat exchanger;

[0006] Its characteristics are:

[0007] The upper portion of the first channel has a gas phase channel extending from outside to inside and communicating with the first channel. The inner port of the gas phase channel is openly communicated with the top central portion of the first channel.

[0008] During heat exchange, the gaseous medium generated in the first channel can flow directly inward through the gaseous channel and through the opening at the top center of the first channel, and be discharged upward through the cold medium outlet pipe. The entire process can reduce vapor resistance and facilitate the discharge of the gaseous medium.

[0009] In practical applications, the cold medium can be a water medium, and steam is generated as a gas phase medium after heat exchange between the cold medium and the hot medium.

[0010] Preferably, the upper part of the first channel is provided with second perforations penetrating the thickness of the first channel side wall layer by layer from the outer circle to the inner circle, and the second perforations on the inner and outer adjacent circles are aligned along the radial direction of the first channel to form the above-mentioned gas phase channel.

[0011] In order to further reduce the vapor resistance, it is also preferred that the gas phase channel extends along the circumference of the first channel and is annular.

[0012] Preferably, the spiral plate heat exchanger includes:

[0013] The shell includes a vertically arranged cylinder, an upper end cover provided at the upper end of the cylinder, and a lower end cover provided at the lower end of the cylinder. The upper end cover is provided with a central through hole to form a ring shape, and the above-mentioned cold medium outlet pipe is provided above the upper end cover. The lower end cover is provided with a middle through hole to form a ring shape, and the above-mentioned hot medium pipe 1 is provided below the lower end cover. The above-mentioned cold medium inlet pipe and hot medium pipe 2 are provided on the side of the cylinder;

[0014] A central tube is vertically arranged in the shell, and its upper and lower ends are respectively arranged corresponding to the central through hole of the upper end cover and the middle through hole of the lower end cover;

[0015] a partition disposed in the central tube and circumferentially dividing the interior space of the central tube into a first independent space extending vertically, open at the top and closed at the bottom, and a second independent space open at the bottom and closed at the top, wherein through holes are provided on the side walls of the central tube corresponding to the first and second independent spaces;

[0016] Two spiral plates are vertically arranged in the cylinder body and constrained between the upper end cover and the lower end cover and the outer periphery of the central cylinder, and are rolled from the inside to the outside along the circumference to form adjacent first spiral channels and second spiral channels. The first spiral channel has the above-mentioned gas phase channel, and the inner port of the first spiral channel is connected with the first independent space through the corresponding through hole to form the above-mentioned first channel, and the inner port of the second spiral channel is connected with the second independent space through the corresponding through hole to form the above-mentioned second channel.

[0017] In the present invention, the spiral plates are not limited to two. For example, there may be four spiral plates to form four adjacent spiral channels. The cold medium passes through two of the spaced spiral channels, and the hot medium passes through the other two spaced spiral channels, so that the cold and hot media are alternately arranged in their respective corresponding spiral channels to achieve heat exchange.

[0018] Preferably, the height of the upper edge of the first spiral channel gradually decreases from the outer circle to the inner circle, and the outer circle of the upper edge is in contact with the lower surface of the upper end cover, and the portion within the outer circle of the upper edge is spaced apart from and opposite to the lower surface of the upper end cover, forming the above-mentioned gas phase channel with an open inner circle and a closed outer circle;

[0019] The upper end edge of the central tube is located below the upper end cover to expose the inner ring opening of the gas phase channel.

[0020] In this way, the gaseous medium formed in the outer circle of the first spiral channel can directly flow inwardly through the gaseous channel and be output.

[0021] To improve structural stability, the lower surface of the upper end cap is preferably provided with at least two radially extending pressure blocks spaced circumferentially. The lower surfaces of the pressure blocks gradually slope downward from the outside to the inside and align with the upper edges of the corresponding first spiral channels. This pressure block constrains the spiral plate, preventing localized upward displacement of the spiral plate. Furthermore, the placement of the pressure blocks minimizes the impact on steam flow.

[0022] Preferably, the pressing block is provided with at least two transversely penetrating first through holes spaced apart along its extension direction to connect the spaces on both sides of the pressing block, thereby further reducing the impact of the pressing block on the fluidity of the gas phase medium.

[0023] The above-mentioned partition can adopt an existing partition plate. In order to reduce the space occupied by the partition itself in the central tube, preferably, the partition includes a partition extending up and down, which has a first side and a second side that are opposite and extend along the axial direction of the central tube. The first side and the second side are respectively connected to the inner circumferential surface of the corresponding central tube, and the partition is in an arc shape from the first and second sides to the center of the two gradually arching toward the center of the central tube. The bottom of the inner space of the partition is closed by the first end plate to form the above-mentioned first independent space, and the top of the outer space of the partition is closed by the second end plate to form the above-mentioned second independent space.

[0024] Compared with the existing partition plates, the arc-shaped partition in the present invention has better stress resistance. Under the same stress conditions, the cold and hot fluids in the central tube can be separated by a thinner partition, thereby reducing the space in the central tube occupied by the partition itself.

[0025] Preferably, the through hole corresponding to the first independent space is located at the bottom of the first independent space and above the first end plate.

[0026] Preferably, there are two partitions, which are arranged at intervals along the circumferential direction, and the bottom of the inner space of each partition is closed by its own first end plate to form the above-mentioned first independent space.

[0027] Compared with the prior art, the advantages of the present invention are: by arranging a gas phase channel extending from the outside to the inside and connected to the first channel in the first channel, the inner port of the gas phase channel is connected to the opening of the top central part of the first channel. In this way, during heat exchange, the gas phase medium generated in the first channel can directly flow inward through the gas phase channel and pass through the opening of the top central part of the first channel, and be discharged upward through the cold medium outlet pipe. The vapor resistance can be reduced in the whole process, which is conducive to the discharge of the gas phase medium. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Figure 1 This is a schematic structural diagram of a spiral plate heat exchanger according to the first embodiment of the present invention;

[0029] Figure 2 This is a partial structural cross-sectional view of a spiral plate heat exchanger according to the first embodiment of the present invention;

[0030] Figure 3 Schematic diagram of the structure of the pressing block of the first embodiment of the present invention;

[0031] Figure 4 for Figure 2 Bottom view of the middle and upper end cover and the pressing block;

[0032] Figure 5 This is a schematic structural diagram of the spiral plate corresponding to the first spiral channel after unfolding according to the first embodiment of the present invention;

[0033] Figure 6 This is another partial structural cross-sectional view of the spiral plate heat exchanger according to the first embodiment of the present invention;

[0034] Figure 7 This is another partial structural cross-sectional view of the spiral plate heat exchanger according to the first embodiment of the present invention;

[0035] Figure 8 A top view of the central tube and the partition of the first embodiment of the present invention;

[0036] Figure 9 This is a schematic structural diagram of a spiral plate heat exchanger according to the second embodiment of the present invention;

[0037] Figure 10 This is a partial structural cross-sectional view of a spiral plate heat exchanger according to the second embodiment of the present invention;

[0038] Figure 11 for Figure 10 Enlarged view of part A in the middle. DETAILED DESCRIPTION

[0039] The present invention will be described in further detail below with reference to the accompanying drawings and embodiments.

[0040] Example 1:

[0041] like Figures 1 to 8 As shown, a preferred embodiment 1 of a spiral plate heat exchanger of the present invention is provided. The spiral plate heat exchanger is vertically arranged, and has a first channel 101 and a second channel 102 adjacent to each other and arranged spirally from the inside to the outside. The outer port of the first channel 101 is connected to the cold medium inlet pipe 111 on the side of the heat exchanger. The top central part of the first channel 101 is open and connected to the cold medium outlet pipe 112 at the top of the heat exchanger, and the top outer portion of the first channel 101 is closed; the bottom central part of the second channel 102 is open and connected to the hot medium pipe 1 113 at the bottom of the heat exchanger. The bottom outer portion of the second channel 102 is closed, and the outer port of the second channel 102 is connected to the hot medium pipe 2 114 on the side of the heat exchanger.

[0042] Specifically, the spiral plate heat exchanger of this embodiment includes a shell 11 , a central tube 12 , a partition 13 and a spiral plate 14 .

[0043] The shell 11 includes a vertically arranged cylinder, an upper end cover 115 located at the upper end of the cylinder, and a lower end cover 118 located at the lower end of the cylinder. The upper end cover 115 is provided with a central through hole 1150 to form a ring shape, and the above-mentioned cold medium outlet pipe 112 is located above the upper end cover 115. The lower end cover is provided with a middle through hole 1180 to form a ring shape, and the above-mentioned hot medium pipe 1 13 is located below the lower end cover 118. The side wall of the cylinder is provided with the above-mentioned cold medium inlet pipe 111 and hot medium pipe 2 114, with the cold medium inlet pipe 111 located below the hot medium pipe 2 114. At the same time, a non-condensable gas outlet pipe 117 is provided on the side wall of the cylinder corresponding to the upper end of the second channel 102. For details, please refer to Figure 7 .

[0044] The central tube 12 is vertically disposed in the housing 11 .

[0045] like Figure 2 、 6As shown in Figures 8 and 8, the partition 13 is arranged in the central tube 12, and divides the internal space of the central tube 12 into a first independent space 121 extending up and down, open at the top and closed at the bottom, and a second independent space 122 with an open bottom and closed at the top, and through holes are provided on the side walls of the central tube 12 corresponding to the first and second independent spaces. Specifically, the partition 13 includes a vertically extending partition 131 having a first side 1311 and a second side 1312 that oppose each other and extend axially along the center tube 12. The first side 1311 and the second side 1312 are respectively engaged with the inner circumferential surface of the corresponding center tube 12. The partition 131 is in an arc shape that gradually rises toward the center of the center tube 12 from the first and second side edges to the center between them, with the central angle corresponding to the arc being less than 180°. The bottom of the space within the partition 131 is closed by a first end plate 132 to form the aforementioned first independent space 121. The aforementioned through-hole corresponding to the first independent space 121 is located at the bottom of the first independent space 121 and above the first end plate 132. The top of the space outside the partition 131 is closed by a second end plate 133 to form the aforementioned second independent space 122. In this embodiment, there are two partitions 131 , which are spaced apart along the circumferential direction. The bottom of the inner space of each partition 131 is closed by its own first end plate 132 to form the above-mentioned first independent space 121 .

[0046] There are two spiral plates 14, both of which are located inside the shell 11 and on the outer periphery of the central tube 12. Both are supported on the lower end plate and are rolled from the inside out along the circumference to form adjacent first spiral channels 141 and second spiral channels 142. The inner port of the first spiral channel 141 is connected to the first independent space 121 through a corresponding through hole to form the first channel 101 mentioned above. The inner port of the second spiral channel 142 is connected to the second independent space 122 through a corresponding through hole to form the second channel 102 mentioned above. At the same time, the height of the upper edge of the first spiral channel 141 gradually decreases from the outer circle to the inner circle (it is rolled from a right-angled trapezoidal plate body, please refer to the details). Figure 5 ), and the outer ring of the upper edge is in contact with the lower surface of the upper end cover 115, thereby forming a gas phase channel 110 with an open inner ring and a closed outer ring between the upper edge of the first spiral channel 141 and the lower surface of the upper end cover 115. The upper edge of the central tube 12 is located below the upper end cover 115, exposing the inner ring opening of the gas phase channel 110. As a result, the gas phase formed by the outer ring of the first spiral channel 141 can flow directly inward through the gas phase channel 110 and be discharged, reducing vapor resistance.

[0047] To constrain the spiral plate, at least two radially extending pressure blocks 116 are circumferentially spaced apart on the lower surface of the upper end cap 115. The lower surfaces of these pressure blocks 116 gradually slope downward from the outside to the inside, aligning with the upper edges of the corresponding first spiral channels 141. Each pressure block 116 is also provided with at least two transversely extending first through-holes 1160 spaced apart along its extension direction to connect the spaces on either side of the pressure block 116. Therefore, the placement of the pressure blocks 116 does not affect the flow of the gaseous medium.

[0048] During heat exchange, the hot medium enters the second channel 102 of the spiral plate heat exchanger 1 through the hot medium pipe 113. The cold medium (such as external water) enters the first channel 101 of the spiral plate heat exchanger 1 through the cold medium inlet pipe 111. After exchanging heat with the hot medium in the second channel 102, the temperature rises and it vaporizes. The vaporized steam flows upward and inward through the gas phase channel 110 at the top of the first channel 101. It then flows upward through the open top center portion of the first channel 101 and is discharged through the cold medium outlet pipe 112. During the entire heat exchange operation, because the spiral plate heat exchanger 1 is arranged vertically and the top center portion of the first channel 101 is open, the vaporized steam can pass quickly and be discharged upward, without forming a vapor resistance in the heat exchanger.

[0049] Example 2:

[0050] like Figures 9-11 The figure shows a preferred embodiment 2 of a spiral plate heat exchanger of the present invention. This embodiment is essentially the same as the first embodiment, except that the upper end of the first spiral channel 141 is provided with second through-holes 1410 extending through the plate thickness, layer by layer from the outer circle to the inner circle. The second through-holes 1410 on adjacent inner and outer circles are aligned radially with respect to the first channel 101, forming a radially extending gas phase channel 110. The upper edge of the central tube 12 is positioned below the upper end cover 115, exposing the second through-holes 1410. This allows the gas phase formed in the outer circle of the first spiral channel 141 to flow inward through each second through-hole 1410, reducing vapor resistance.

[0051] In the specification and claims of the present invention, directional terms such as "front," "back," "up," "down," "left," "right," "side," "top," and "bottom" are used to describe various exemplary structural parts and components of the present invention. However, these terms are used herein for convenience of description only and are based on the exemplary orientations shown in the accompanying drawings. Since the embodiments disclosed in the present invention can be arranged in different orientations, these directional terms are intended for illustrative purposes only and should not be construed as limiting. For example, "up" and "down" are not necessarily limited to directions opposite to or consistent with the direction of gravity.

[0052] The term "vertical" is also used in the specification and claims of the present utility model, which means basically along the up and down direction, and is not limited to the vertical direction, and can also be slightly deviated from the vertical direction.

[0053] The term "radial" is also used in the specification and claims of the present invention, which means basically along the inward and outward direction, and is not limited to the radial direction passing through the center of the circle, and can also be slightly deviated from the radial direction.

Claims

1. A spiral plate heat exchanger, wherein the first channel (101) and the second channel (102) are adjacent and arranged in a spiral from the outside to the inside, the first channel (101) and the second channel (102) are both arranged vertically, and the top central portion of the first channel (101) is open and communicated with the cold medium outlet pipe (112) at the top of the heat exchanger, the top peripheral portion of the first channel (101) is closed, and the outer port of the first channel (101) is connected to the cold medium inlet pipe (111) at the side of the heat exchanger; the bottom central portion of the second channel (102) is open and communicated with the hot medium pipe 1 (113) at the bottom of the heat exchanger, and the outer port of the second channel (102) is connected to the hot medium pipe 2 (114) at the side of the heat exchanger; Its characteristics are: The upper portion of the first channel (101) has a gas phase channel extending from outside to inside and communicating with the first channel (101), and the inner port of the gas phase channel (110) is openly communicated with the top central portion of the first channel (101).

2. The spiral plate heat exchanger according to claim 1, characterized in that: The upper part of the first channel (101) is provided with second through-holes (1410) penetrating the thickness of the side wall of the first channel (101) layer by layer from the outer circle to the inner circle, and the second through-holes (1410) on the inner and outer adjacent circles are aligned along the radial direction of the first channel (101) to form the above-mentioned gas phase channel (110).

3. The spiral plate heat exchanger according to claim 1, characterized in that: The gas phase channel (110) also extends along the circumference of the first channel (101) and is annular.

4. The spiral plate heat exchanger according to claim 3, characterized in that: The spiral plate heat exchanger includes: The shell (11) includes a vertically arranged cylinder, an upper end cover (115) provided at the upper end of the cylinder, and a lower end cover (118) provided at the lower end of the cylinder. The upper end cover (115) is provided with a central through hole (1150) to form a ring shape, and the upper end cover (115) is provided with the above-mentioned cold medium outlet pipe (112). The lower end cover (118) is provided with a middle through hole (1180) to form a ring shape, and the lower end cover (118) is provided with the above-mentioned hot medium pipe 1 (113). The side of the cylinder is provided with the above-mentioned cold medium inlet pipe (111) and hot medium pipe 2 (114). A central tube (12) is vertically arranged in the housing (11), and its upper and lower ends are respectively arranged corresponding to the central through hole (1150) of the upper end cover (115) and the middle through hole (1180) of the lower end cover (118); A separator (13) is provided in the central tube (12) and divides the internal space of the central tube (12) into a first independent space (121) extending vertically, open at the top and closed at the bottom, and a second independent space (122) open at the bottom and closed at the top, and through holes are provided on the side walls of the central tube (12) corresponding to the first and second independent spaces; Two spiral plates (14) are vertically arranged in the cylinder body and constrained between the upper end cover (115) and the lower end cover (118) and the outer periphery of the central cylinder (12), and are rolled from the inside to the outside along the circumference to form adjacent first spiral channels (141) and second spiral channels (142). The first spiral channel (141) has the above-mentioned gas phase channel (110), and the inner port of the first spiral channel (141) is connected to the first independent space (121) through a corresponding through hole to form the above-mentioned first channel (101), and the inner port of the second spiral channel (142) is connected to the second independent space (122) through a corresponding through hole to form the above-mentioned second channel (102).

5. The spiral plate heat exchanger according to claim 4, characterized in that: The height of the upper edge of the first spiral channel (141) gradually decreases from the outer circle to the inner circle, and the outer circle of the upper edge is in contact with the lower surface of the upper end cover (115), and the portion inside the outer circle of the upper edge is spaced apart from and opposite to the lower surface of the upper end cover (115), forming the above-mentioned gas phase channel (110) with an open inner circle and a closed outer circle; The upper end edge of the central tube (12) is located below the upper end cover (115) to expose the inner ring opening of the gas phase channel (110).

6. The spiral plate heat exchanger according to claim 5, characterized in that: At least two radially extending pressing blocks (116) are provided on the lower surface of the upper end cover (115) at intervals along the circumferential direction, and the lower surface of the pressing block (116) gradually slopes downward from the outside to the inside and fits with the upper end edge of the corresponding first spiral channel (141).

7. The spiral plate heat exchanger according to claim 6, characterized in that: At least two transversely penetrating first through holes (1160) are provided on the pressing block (116) at intervals along its extension direction to connect the spaces on both sides of the pressing block (116).

8. The spiral plate heat exchanger according to claim 4, characterized in that: The partition (13) includes a partition (131) extending up and down, which has a first side (1311) and a second side (1312) opposite to each other and extending along the axial direction of the central tube (12), the first side (1311) and the second side (1312) are respectively connected to the inner peripheral surface of the corresponding central tube (12), and the partition (131) is in the shape of an arc that gradually arches from the first and second side edges to the center of the two sides toward the center of the central tube (12), the bottom of the inner space of the partition (131) is closed by the first end plate (132) to form the above-mentioned first independent space (121), and the top of the outer space of the partition (131) is closed by the second end plate (133) to form the above-mentioned second independent space (122).

9. The spiral plate heat exchanger according to claim 8, characterized in that: The through hole corresponding to the first independent space (121) is located at the bottom of the first independent space (121) and above the first end plate (132).

10. The spiral plate heat exchanger according to claim 8, characterized in that: There are two partitions (131) arranged at intervals along the circumferential direction, and the bottom of the inner space of each partition (131) is closed by a respective first end plate (132) to form the above-mentioned first independent space (121).

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