Shell and tube heat exchanger

Abstract

The invention provides a shell and tube heat exchanger, and relates to the technical field of heat exchange. The shell-and-tube heat exchanger comprises a barrel, a heat exchange tube set and a liquid homogenizing plate. The barrel is provided with a liquid inlet; the heat exchange tube group is mounted in the cylinder body; the liquid homogenizing plate is mounted in the cylinder body and is positioned between the heat exchange tube group and the liquid inlet; the liquid uniformizing plate comprises a first plate body and second plate bodies, the second plate bodies are connected to the two sides of the first plate body in the first direction, the first plate body and the liquid inlet are oppositely arranged in the thickness direction of the first plate body, the first plate body and the second plate bodies are arranged at an angle and define a wrapping space, and at least part of layers of heat exchange pipe sets are located in the wrapping space. The first plate body is provided with a plurality of first liquid uniformizing holes which are distributed at intervals, the second plate body is provided with a plurality of second liquid uniformizing holes which are distributed at intervals, and the first liquid uniformizing holes and the second liquid uniformizing holes are respectively communicated with the wrapping space. The second plate body can guide part of the refrigerant to flow and flow out of the second liquid uniformizing holes so as to exchange heat with the heat exchange tube set far away from the liquid inlet, and the heat exchange efficiency is improved.

Description

Technical Field

[0001] The present application relates to the field of heat exchange technology, and in particular to a shell and tube heat exchanger. Background Art

[0002] In a flooded evaporator (i.e., shell and tube heat exchanger), water flows through the tube side and refrigerant flows through the shell side, and evaporates on the surface of the heat exchange tube (i.e., tube side). The refrigerant of a flooded evaporator enters the shell side from the liquid inlet at the bottom of the cylinder, passes through the liquid equalizing holes on the liquid equalizing plate, and then exchanges heat with the heat exchange tubes in the cylinder. Limited by the existing liquid equalizing plate structure, the heat exchange tubes close to the liquid inlet first exchange heat with the refrigerant, and the heat exchange tubes far from the liquid inlet exchange heat with the refrigerant after heat exchange again, so that the temperature difference between the refrigerant and the heat exchange tubes far from the liquid inlet is small, and the heat exchange efficiency of the heat exchange tubes far from the liquid inlet cannot be maximized. Summary of the invention

[0003] Based on this, it is necessary to provide a shell and tube heat exchanger to improve the heat exchange efficiency of the heat exchange tubes.

[0004] The shell and tube heat exchanger includes a cylinder, a heat exchange tube group arranged in multiple layers at intervals, and a liquid equalizing plate; the cylinder is provided with a liquid inlet; the heat exchange tube group is installed in the cylinder; the liquid equalizing plate is installed in the cylinder and is located between the heat exchange tube group and the liquid inlet; the liquid equalizing plate includes a first plate body and a second plate body, the second plate body is connected to both sides of the first plate body along a first direction, and along the thickness direction of the first plate body, the first plate body and the liquid inlet are arranged opposite to each other, the first plate body and the second plate body are arranged at an angle and surround to form an enclosing space; wherein, at least part of the layers of the heat exchange tube group are located in the enclosing space; the first plate body is provided with a plurality of first liquid equalizing holes arranged at intervals, and the second plate body is provided with a plurality of second liquid equalizing holes arranged at intervals, and the first liquid equalizing holes and the second liquid equalizing holes are respectively connected to the enclosing space.

[0005] It is understandable that part of the refrigerant can flow out of the first liquid balancing hole on the first plate body and enter the surrounding space, which is conducive to uniform heat exchange between the refrigerant and the heat exchange tube group near the liquid inlet. The second plate body can guide another part of the refrigerant to flow along the surface of the second plate body and flow out of the second liquid balancing hole, so that the refrigerant can exchange heat with the heat exchange tube far away from the liquid inlet. The heat exchange performance of the heat exchange tube far away from the liquid inlet is fully utilized to enhance the overall heat exchange efficiency of the heat exchange tube group in the cylinder.

[0006] In one embodiment, along the second direction, the first plate body and the second plate body are both constructed with a covering portion and a drainage portion, and the drainage portion is located on both sides of the covering portion; the covering portion located on the first plate body is arranged opposite to the liquid inlet along its own thickness direction; wherein the first liquid equalizing hole is located in the drainage portion of the first plate body, and the second liquid equalizing hole is located in the drainage portion of the second plate body.

[0007] It can be understood that the cover portion can block the flow of refrigerant so that more refrigerant can flow to the drainage portion, and the drainage portion can guide the refrigerant to flow along the contact surface to contact with more heat exchange tubes in the heat exchange tube group, thereby improving heat exchange efficiency.

[0008] In one of the embodiments, in the drainage portion, along the first direction and / or the second direction, the spacing between any two adjacent first liquid equalizing holes is not less than the spacing between any two adjacent second liquid equalizing holes.

[0009] It can be understood that the spacing between the first liquid balancing holes is not less than the spacing between the second liquid balancing holes, and the number of first liquid balancing holes that can be set is less than that of the second liquid balancing holes, which is conducive to more refrigerant flowing out of the second liquid balancing holes.

[0010] In one of the embodiments, in the drainage portion, along the first direction, the spacing between any two adjacent first liquid equalizing holes is d1, and the spacing between any two adjacent second liquid equalizing holes is d2, d1≥2d2; and / or, in the drainage portion, along the second direction, the spacing between any two adjacent first liquid equalizing holes is greater than the spacing between any two adjacent second liquid equalizing holes.

[0011] It can be understood that, in this way, the number of the second liquid balancing holes is arranged more densely, more refrigerant can flow out from the second liquid balancing holes, and at the same time, it is convenient to process the first plate body and the second plate body.

[0012] In one embodiment, in the drainage portion, the plurality of the first liquid equalizing holes and the plurality of the second liquid equalizing holes are evenly spaced along the first direction and / or the second direction.

[0013] It can be understood that the evenly spaced arrangement facilitates processing and helps reduce processing costs.

[0014] In one of the embodiments, the liquid equalizing plate includes a baffle, which is connected to one end of the second plate body away from the first plate body and is arranged at an angle to the second plate body; the baffle extends along the first direction and away from the first plate body; the baffle can abut against the inner wall of the cylinder body, and the baffle, the second plate body, the first plate body and the inner wall are arranged to form a liquid equalizing space; the liquid equalizing space is connected to the surrounding space through the first liquid equalizing hole and the second liquid equalizing hole.

[0015] It can be understood that the baffle can limit the flow direction of the refrigerant, so that the refrigerant can only flow out from the liquid equalization holes in the first plate body and the second plate body, thereby ensuring the liquid equalization effect.

[0016] In one of the embodiments, the first plate is bent along its thickness direction toward the surrounding space.

[0017] It can be understood that the arrangement in which the first plate body is bent toward the surrounding space increases the space between the first plate body and the liquid inlet to accommodate more refrigerant, thereby facilitating smooth flow of the refrigerant.

[0018] In one embodiment, the radius of the cylinder is R, the second plate is configured to be an arc, the radius of the second plate is r, and r is in the range of 0.75R to 0.9R.

[0019] It is understandable that the second plate body is arranged in an arc shape to facilitate the refrigerant to flow along the arc surface of the second plate body, so as to enhance the drainage effect on the refrigerant. The radius of the second plate body is arranged so as to leave a certain gap between the second plate body and the cylinder body, so as to facilitate the flow of the refrigerant.

[0020] In one embodiment, the height of the multi-layer heat exchange tube group in the cylinder is h, h=R~1.2R, and the height of the liquid equalizing plate is H, and the range of H is 0.5h~1.1h.

[0021] It can be understood that the height of the liquid equalizing plate is set to correspond to the height of the multi-layer heat exchange tube group, which is conducive to guiding the refrigerant to the heat exchange tubes away from the liquid inlet and avoiding material waste.

[0022] In one embodiment, the dimension of the liquid inlet along the first direction is c, c<R, the dimension of the first plate along the first direction is b, and the range of b is 1.5c~2.7c.

[0023] It can be understood that the size setting of the first plate body can ensure that the first plate body can be covered on the liquid inlet, and ensure that the heat exchange tubes near the liquid inlet can evenly exchange heat with the refrigerant. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the conventional technology, the drawings required for use in the embodiments or the conventional technology descriptions are briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0025] Figure 1 A schematic diagram of the structure of a liquid balancing plate in a shell and tube heat exchanger provided in this application;

[0026] Figure 2 A top view of a liquid balancing plate in a shell and tube heat exchanger provided in the present application;

[0027] Figure 3 for Figure 2 A partial enlarged view of the middle A;

[0028] Figure 4 A front view of a liquid balancing plate in a shell and tube heat exchanger provided in the present application;

[0029] Figure 5 Side view of a shell and tube heat exchanger provided for this application.

[0030] Figure numerals: 1000, shell and tube heat exchanger; 1001, liquid equalizing space; 1002, liquid inlet; 200, cylinder; 300, heat exchange tube group; 3001, heat exchange tube; 100, liquid equalizing plate; 101, cover part; 102, drainage part; 103, surrounding space; 104, liquid equalizing hole; 10, first plate body; 11, first liquid equalizing hole; 20, second plate body; 21, second liquid equalizing hole; 30, baffle. DETAILED DESCRIPTION

[0031] In order to make the above-mentioned purposes, features and advantages of the present application more obvious and easy to understand, the specific implementation methods of the present application are described in detail below in conjunction with the accompanying drawings. In the following description, many specific details are set forth to facilitate a full understanding of the present application. However, the present application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without violating the connotation of the present application, so the present application is not limited by the specific embodiments disclosed below.

[0032] It should be noted that when a component is referred to as being "fixed to" or "disposed on" another component, it may be directly on the other component or there may also be a central component. When a component is considered to be "connected to" another component, it may be directly connected to the other component or there may be a central component at the same time. The terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used in the specification of this application are for illustrative purposes only and do not represent the only implementation method.

[0033] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In the description of this application, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0034] In the present application, unless otherwise clearly specified and limited, a first feature being “above” or “below” a second feature may mean that the first feature is directly in contact with the second feature, or the first feature and the second feature are indirectly in contact through an intermediate medium. Moreover, a first feature being “above”, “above” or “above” a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature being “below”, “below” or “below” a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0035] Unless otherwise defined, all technical and scientific terms used in the specification of this application have the same meaning as those commonly understood by those skilled in the art to which this application belongs. The terms used in the specification of this application are only for the purpose of describing specific embodiments and are not intended to limit this application. The term "and / or" used in the specification of this application includes any and all combinations of one or more related listed items.

[0036] See also Figures 1 to 5 The present application provides a shell and tube heat exchanger 1000, which includes a cylinder 200, a heat exchange tube group 300 arranged at intervals in multiple layers, and a liquid balancing plate 100. The cylinder 200 is provided with a liquid inlet 1002; the heat exchange tube group 300 is installed in the cylinder 200; the liquid balancing plate 100 is installed in the cylinder 200 and is located between the heat exchange tube group 300 and the liquid inlet 1002. The liquid balancing plate 100 includes a first plate body 10 and a second plate body 20, the second plate body 20 is connected to both sides of the first plate body 10 along a first direction, and along the thickness direction of the first plate body 10, the first plate body 10 and the liquid inlet 1002 are arranged opposite to each other, and the first plate body 10 and the second plate body 20 are arranged at an angle and enclosed to form a surrounding space 103; wherein, at least part of the layers of the heat exchange tube group 300 are located in the surrounding space 103. The liquid equalizing plate 100 is provided with a plurality of liquid equalizing holes 104 penetrating the liquid equalizing plate 100 , and the plurality of liquid equalizing holes 104 are arranged at intervals; the liquid equalizing hole 104 penetrating the first plate body 10 is defined as a first liquid equalizing hole 11 , and the liquid equalizing hole 104 penetrating the second plate body 20 is defined as a second liquid equalizing hole 21 , and the first liquid equalizing hole 11 and the second liquid equalizing hole 21 are respectively connected to the surrounding space 103 .

[0037] For the sake of convenience of explanation, the projection of the liquid equalizing plate 100 along the thickness direction of the first plate body 10 is a rectangle, the width direction of the rectangle is the first direction, the length direction of the rectangle is the second direction, the first direction is defined as the x-axis, the second direction is defined as the y-axis, and the thickness direction of the first plate body 10 is defined as the z-axis for explanation.

[0038] In this way, the liquid balancing plate 100 is provided with a plurality of liquid balancing holes 104 so as to divert the refrigerant input from the liquid inlet 1002, and the refrigerant flows out from each liquid balancing hole 104 to increase the contact area between the refrigerant and the heat exchange tube group 300, and promote uniform heat exchange. Further, the liquid balancing plate 100 includes a first plate body 10 and a second plate body 20, which form a surrounding space 103, so that the refrigerant diffuses along the second plate body 20 after entering from the liquid inlet 1002, and passes through the liquid balancing holes 104 into the surrounding space 103 to exchange heat with the heat exchange tube group 300 located in the surrounding space 103, which is beneficial to increase the contact area between the refrigerant and the heat exchange tube group 300 during the initial heat exchange, thereby improving the heat exchange efficiency.

[0039] Specifically, the first plate body 10 can directly output part of the refrigerant entering from the liquid inlet 1002 from the first liquid balancing hole 11, so that the part of the refrigerant exchanges heat with the heat exchange tube group 300 near the liquid inlet 1002. The second plate body 20 can guide another part of the refrigerant, guide the refrigerant to flow along the second plate body 20 and flow out from the second liquid balancing hole 21, so that the part of the refrigerant can directly exchange heat with the heat exchange tube group 300 far away from the liquid inlet 1002. This allows the refrigerant to exchange heat with more heat exchange tube groups 300 at the same time, which is conducive to improving the heat exchange efficiency.

[0040] like Figure 2 As shown, in a further embodiment, along the second direction, the first plate body 10 and the second plate body 20 are both constructed with a cover portion 101 and a drainage portion 102, and the cover portion 101 is connected to the drainage portion 102 on both sides along the second direction, wherein the first liquid equalizing hole 11 is arranged in the drainage portion 102 of the first plate body 10, and the second liquid equalizing hole 21 is arranged in the drainage portion 102 of the second plate body 20.

[0041] In actual use, the cover portion 101 located on the first plate body 10 is arranged opposite to the liquid inlet 1002 along its thickness direction, and can be specifically arranged opposite to it. Therefore, the cover portion can block the flow of the refrigerant directly input from the liquid inlet 1002, so that more refrigerant can flow to the drainage portion 102 along the y-axis (i.e., the second direction), and the drainage portion 102 will continue to drain the refrigerant along the y-axis, so that the refrigerant can flow out from multiple liquid balancing holes 104. Different heat exchange tube groups 300 are correspondingly arranged at different liquid balancing holes 104, which is conducive to increasing the heat exchange area and improving the heat exchange efficiency.

[0042] In a further embodiment, in the drainage portion 102, along the first direction and / or the second direction, the spacing between any two adjacent first liquid balancing holes 11 is not less than the spacing between any two adjacent second liquid balancing holes 21. In this way, the spacing between the second liquid balancing holes 21 is smaller, while the spacing between the first liquid balancing holes 11 is larger, so as to appropriately reduce the flow of the refrigerant directly passing through the first plate body 10, facilitate more refrigerant to flow along the second plate body 20, and improve the drainage effect to promote heat exchange.

[0043] like Figure 3 As shown, in a specific embodiment, in the drainage portion 102, along the first direction, the spacing between any two adjacent first liquid balancing holes 11 is d1, and the spacing between any two adjacent second liquid balancing holes 21 is d2, and d1≥2d2. In the drainage portion 102, along the second direction, the spacing between any two adjacent first liquid balancing holes 11 is greater than the spacing between any two adjacent second liquid balancing holes 21. In this way, the second plate body 20 can be provided with more second liquid balancing holes 21, so that more refrigerant can flow out from the second liquid balancing holes 21. Exemplarily, d1=2d2, 3d2 or 4d2.

[0044] like Figures 1 to 3 As shown, in one embodiment, in the drainage portion 102, a plurality of first liquid balancing holes 11 and a plurality of second liquid balancing holes 21 are evenly spaced along the first direction and / or the second direction. In this way, when punching along the first direction and / or the second direction, the spacing of each punching process is the same, and there is no need to adjust the punching spacing additionally, which is conducive to rapid production and improves production efficiency.

[0045] like Figure 1 and Figure 2 As shown, in a specific embodiment, the liquid balancing plate includes a baffle 30, which is connected to one end of the second plate body 20 away from the first plate body 10 and is arranged at an angle to the second plate body 20; the baffle 30 extends in a first direction opposite to the first plate body 10. In actual use, the baffle 30 can abut against the inner wall of the cylinder 200, and the baffle 30, the second plate body 20, the first plate body 10 and the inner wall of the cylinder are surrounded to form a liquid balancing space 1001 for the refrigerant, and the liquid balancing space 1001 is connected to the surrounding space 103 through the first liquid balancing hole 11 and the second liquid balancing hole 21. In this way, the baffle 30 can block the flow of the refrigerant so that after the refrigerant enters the liquid equalizing space 1001, it can only flow out from the liquid equalizing hole 104, so as to ensure the liquid equalizing effect and prevent part of the fluid from directly flowing out from the end of the second plate body 20 away from the first plate body 10, so that the refrigerant can evenly exchange heat with the heat exchange tube group 300 away from the liquid inlet 1002, thereby further improving the heat exchange efficiency.

[0046] like Figure 4As shown, in a specific embodiment, the first plate body 10 is bent along its thickness direction toward the surrounding space 103. In this way, it is beneficial to increase the distance between the first plate body 10 and the liquid inlet 1002, and increase the space between the first plate body 10 and the inner cylinder wall around the liquid inlet 1002, so as to accommodate part of the refrigerant, reserve time for the refrigerant to pass through the liquid balancing hole 104, and ensure that the refrigerant can smoothly enter the surrounding space 103. At the same time, it is beneficial to have sufficient pressure to flow into the space between the second plate body 20 and the inner cylinder wall, promoting drainage.

[0047] like Figure 4 As shown, in a specific embodiment, the second plate body 20 is configured to be arc-shaped to form a smooth curved surface, thereby reducing the resistance to the flow of the refrigerant and enhancing the drainage effect on the refrigerant.

[0048] like Figure 5 As shown, in a specific embodiment, the radius of the cylinder 200 is R, and the radius of the second plate 20 is r, and r ranges from 0.75R to 0.9R. In this way, it is ensured that there is an appropriate space between the second plate 20 and the cylinder 200, and the refrigerant is ensured to flow smoothly on the basis of promoting drainage. For example, r = 0.75R, 0.8R or 0.9R.

[0049] like Figure 5 As shown, in a specific embodiment, each layer of heat exchange tube group 300 has a plurality of heat exchange tubes 3001 arranged at intervals along the first direction, and the multi-layer heat exchange tube group 300 is arranged at intervals along the thickness direction of the first plate body 10. The height of the multi-layer heat exchange tube group 300 in the cylinder 200 is h, h = R ~ 1.2R, for example, h = R, 1.1R or 1.2R, that is, the heat exchange tube group 300 occupies nearly half of the volume of the cylinder 200. Since the boiling of the refrigerant has a certain boiling height, the above arrangement can reserve enough space for the boiling height of the refrigerant.

[0050] Furthermore, the height of the liquid equalizing plate 100 is H, and the range of H is 0.5h~1.1h. In this way, the height of the liquid equalizing plate 100 is adapted to the height of the multi-layer heat exchange tube group 300, ensuring that the liquid equalizing plate 100 can guide the refrigerant to the heat exchange tube 3001 away from the liquid outlet. At the same time, it can also avoid the liquid equalizing plate being too large in size to save materials and help save costs. More specifically, H=0.5h, 0.8h or 1.1h. In actual use, the height of the liquid equalizing plate 100 should be determined according to the actual height of the heat exchange tube group 300.

[0051] like Figure 5As shown, in a specific embodiment, the size of the liquid inlet 1002 along the first direction is c, c < R, and the size of the first plate body 10 along the first direction is b, and the range of b is 1.5c ~ 2.7c. In this way, the first plate body 10 can completely cover the liquid inlet 1002, ensuring that the heat exchange tube 3001 facing the liquid inlet 1002 can evenly exchange heat with the refrigerant, which is conducive to improving the heat exchange efficiency. Exemplarily, b = 1.5c, 2c or 2.7c.

[0052] The technical features of the above-described embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the technical features in the above-described embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0053] The above-described embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the patent application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the scope of patent protection of the present application shall be subject to the attached claims.

Claims

1. A shell and tube heat exchanger, characterized in that: The shell and tube heat exchanger comprises: The cylinder (200) is provided with a liquid inlet (1002); A heat exchange tube group (300) arranged in multiple layers and spaced apart from each other is installed in the cylinder (200); a liquid balancing plate (100) installed in the cylinder (200) and located between the heat exchange tube group (300) and the liquid inlet (1002); the liquid balancing plate (100) comprises a first plate body (10) and a second plate body (20); the second plate body (20) is connected to two sides of the first plate body (10) along a first direction; along the thickness direction of the first plate body (10), the first plate body (10) and the liquid inlet (1002) are arranged opposite to each other; the first plate body (10) and the second plate body (20) are arranged at an angle and enclosed to form a surrounding space (103); In which, at least part of the layers of the heat exchange tube group (300) are located in the surrounding space (103); the first plate body (10) is provided with a plurality of first liquid balancing holes (11) arranged at intervals, and the second plate body (20) is provided with a plurality of second liquid balancing holes (21) arranged at intervals, and the first liquid balancing holes (11) and the second liquid balancing holes (21) are respectively connected to the surrounding space (103).

2. The shell and tube heat exchanger according to claim 1, characterized in that: Along the second direction, the first plate body (10) and the second plate body (20) are both configured with a cover portion (101) and a drainage portion (102), and the drainage portion (102) is located on both sides of the cover portion (101); The cover portion (101) located on the first plate body (10) is arranged opposite to the liquid inlet (1002) along its thickness direction; Wherein, the first liquid balancing hole (11) is located in the drainage portion (102) of the first plate body (10), and the second liquid balancing hole (21) is located in the drainage portion (102) of the second plate body (20).

3. The shell and tube heat exchanger according to claim 2, characterized in that: In the drainage portion (102), along the first direction and / or the second direction, the distance between any two adjacent first liquid equalizing holes (11) is not less than the distance between any two adjacent second liquid equalizing holes (21).

4. The shell and tube heat exchanger according to claim 3, characterized in that: In the drainage portion (102), along the first direction, the distance between any two adjacent first liquid balancing holes (11) is d1, and the distance between any two adjacent second liquid balancing holes (21) is d2, and d1≥2d2; In the drainage portion (102), along the second direction, the distance between any two adjacent first liquid equalizing holes (11) is greater than the distance between any two adjacent second liquid equalizing holes (21).

5. The shell and tube heat exchanger according to claim 2, characterized in that: In the drainage portion (102), a plurality of the first liquid balancing holes (11) and a plurality of the second liquid balancing holes (21) are evenly spaced along the first direction and / or the second direction.

6. The shell and tube heat exchanger according to claim 1, characterized in that: The liquid balancing plate (100) comprises a baffle (30), the baffle (30) being connected to one end of the second plate body (20) away from the first plate body (10), and being arranged at an angle to the second plate body (20); the baffle (30) extending in the first direction away from the first plate body (10); the baffle (30) being capable of abutting against the inner wall of the cylinder body (200), and the baffle (30), the second plate body (20), the first plate body (10) and the inner wall of the cylinder body (200) forming a liquid balancing space (1001); The liquid equalizing space (1001) is connected to the surrounding space (103) through the first liquid equalizing hole (11) and the second liquid equalizing hole (21).

7. The shell and tube heat exchanger according to claim 1, characterized in that: The first plate body (10) is bent along its thickness direction toward the surrounding space (103).

8. The shell and tube heat exchanger according to claim 1, characterized in that: The radius of the cylinder (200) is R, the second plate (20) is configured to be an arc shape, the radius of the second plate (20) is r, and r is in the range of 0.75R to 0.9R.

9. The shell and tube heat exchanger according to claim 8, characterized in that: The height of the multi-layer heat exchange tube group (300) in the cylinder (200) is h, where h=R~1.2R, and the height of the liquid balancing plate (100) is H, where H ranges from 0.5h to 1.1h.

10. The shell and tube heat exchanger according to claim 8, characterized in that: The dimension of the liquid inlet (1002) along the first direction is c, c<R, and the dimension of the first plate (10) along the first direction is b, and the range of b is 1.5c-2.7c.

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