A dual-system shell-and-tube condenser with double working conditions and a regulation method thereof

Abstract

The application relates to the technical field of condensers, in particular to a double-working-condition double-system shell-and-tube condenser and a regulation method thereof. The condenser comprises a first shell cavity and a second shell cavity, the interiors of the first shell cavity and the second shell cavity are respectively provided with a flow feeding pipe and a backflow pipe, and a butt joint cavity is arranged between the first shell cavity and the second shell cavity; a through cavity is fixedly arranged on the inner wall of the butt joint cavity; in the first working condition, the medium in the first shell cavity and the second shell cavity is simultaneously subjected to heat exchange; when the medium in the second shell cavity does not need to be subjected to heat exchange, the second working condition can be entered, at which time the medium in the first shell cavity is subjected to heat exchange only, so that the cooling liquid flow path is reduced.

Description

Technical Field

[0001] This invention relates to the field of condenser technology, specifically to a dual-condition, dual-system shell-and-tube condenser and its control method. Background Technology

[0002] A shell-and-tube condenser is a high-efficiency heat exchange device, mainly composed of a shell and an internal tube bundle. Coolant flows within the tube bundle, while the medium to be cooled flows within the shell, achieving heat exchange. Existing shell-and-tube condensers, such as the shell-and-tube condenser and refrigeration unit disclosed in CN202973672U, include a tubular shell open at both ends. The upper side of the shell has a refrigerant inlet, and the lower side has a liquid outlet. Inside the shell, a condensing tube bundle supported by multiple support plates is horizontally arranged.

[0003] The aforementioned shell-and-tube condenser can only exchange heat with one type of medium at a time, and cannot achieve dual-system processing. Furthermore, it cannot adjust its operating conditions according to the medium, and requires further optimization and improvement. Summary of the Invention

[0004] The purpose of this invention is to provide a dual-condition, dual-system shell-and-tube condenser and its control method to solve the problems mentioned in the background art.

[0005] To achieve the above objectives, the present invention provides the following technical solution: a dual-condition dual-system shell-and-tube condenser, comprising a first shell cavity and a second shell cavity, wherein both the first and second shell cavities are provided with a supply pipe and a return pipe, and a docking clamp cavity is provided between the first and second shell cavities; a manifold shell is fixedly provided on the inner wall of the docking clamp cavity, and a total of four manifold shells are provided, with the ends of the supply pipe and the return pipe respectively connected to a manifold shell individually; the four manifold shells are symmetrically distributed vertically and horizontally, and a condition-changing disc is rotatably installed between the manifold shells, and a sealing ring is provided on the surface of the manifold shell, through which the manifold shell is in sealed contact with the condition-changing disc; the operating conditions are switched by rotating the condition-changing disc. In the first operating condition, the supply pipe in the first shell cavity is directly connected to the supply pipe in the second shell cavity through the condition-changing disc, and at the same time, the return pipe in the second shell cavity is directly connected to the return pipe in the first shell cavity through the condition-changing disc; in the second operating condition, the supply pipe in the first shell cavity is directly connected to the return pipe in the first shell cavity through the condition-changing disc.

[0006] The surface of the variable displacement plate is provided with two independent hole groups. Under the first operating condition, the flow pipe in the first cavity is connected to the flow pipe in the second cavity through one of the independent hole groups; the return pipe in the second cavity is connected to the return pipe in the first cavity through the other independent hole group.

[0007] The surface of the variable speed control panel is provided with a group of interconnecting holes. The end of the interconnecting hole group facing the first cavity is open and the end facing the second cavity is closed. There are two interconnecting hole groups, and an interconnecting cavity is provided between the two interconnecting hole groups to achieve communication. In the second operating condition, the flow supply pipe in the first cavity is connected to the return pipe in the first cavity through the interconnecting hole group and the interconnecting cavity.

[0008] A disc spindle is fixedly installed at the center of the variable speed control disc, and a worm gear is fixedly installed on the disc spindle. A worm portion is meshed with the outside of the worm gear, and a drive shaft is drivenly connected to the worm portion. One end of the drive shaft extends to the outside of the second housing cavity, and the drive shaft and the second housing cavity are sealed.

[0009] Temperature probes are installed in the manifold shells that are connected to the return pipe. A first check valve is installed at the closed end of one of the interconnecting hole groups, and a disconnected pumping assembly is installed at the closed end of the other interconnecting hole group.

[0010] The isolation pump assembly includes a cylindrical shell fixedly mounted on the closed end of the interconnected hole group. An integral embedded tube is fixedly mounted on the cylindrical shell, and a second one-way valve is fixedly installed in the integral embedded tube. A first bypass hole is opened on the integral embedded tube, and the second one-way valve communicates with the interior of the cylindrical shell through the first bypass hole. The second one-way valve is used to restrict the liquid from flowing unidirectionally into the cylindrical shell.

[0011] A sealing plug is fixedly installed at one end of the integrated tube inside the column shell. A pump plug structure is provided inside the column shell, and a sealing top tube is fixedly installed on the pump plug structure. When the pump plug structure moves into place in the direction of the sealing plug, the sealing plug will press against the end of the sealing top tube and seal the sealing top tube.

[0012] A third one-way valve is fixedly installed in the sealed top pipe, and a second bypass hole is connected to the end of the sealed top pipe. The third one-way valve is used to restrict the liquid in the column shell to flow unidirectionally into the second bypass hole. A first elastic element is provided on the side of the pump plug structure facing the sealing rubber plug. A drive assembly is provided on the side of the pump plug structure away from the first elastic element. The drive assembly is used to control the axial movement of the pump plug structure without affecting the rotation of the variable displacement plate.

[0013] The drive assembly includes a limiting bracket and a top shaft that is inserted into the limiting bracket. The limiting bracket is fixedly installed inside the conduit shell. A second elastic element is provided on the outside of the top shaft, which causes the top shaft to tend to move away from the pump plug structure. In the second working condition, the pump plug structure is coaxially aligned with the top shaft. A limiting outer frame is fixedly provided on the limiting bracket. An inclined block is installed in the limiting outer frame. An axial displacement shaft is fixedly provided on the inclined block. One end of the axial displacement shaft extends to the outside of the second shell cavity, and the axial displacement shaft and the second shell cavity are sealed. The axial displacement shaft controls the lifting and lowering of the inclined block, so that the inclined block squeezes and drives the top shaft.

[0014] A control method for a dual-condition dual-system shell-and-tube condenser. The method uses a dual-condition dual-system shell-and-tube condenser. When heat exchange is performed on the medium in the first shell cavity and the second shell cavity at the same time, the feed pipe in the first shell cavity is directly connected to the feed pipe in the second shell cavity through the temperature change plate, and at the same time, the return pipe in the second shell cavity is directly connected to the return pipe in the first shell cavity through the temperature change plate. When only the medium in the first cavity is subjected to heat exchange, the variable displacement plate is rotated so that the supply pipe in the first cavity is directly connected to the return pipe in the first cavity through the variable displacement plate.

[0015] Compared with the prior art, the beneficial effects of the present invention are: The dual-system shell-and-tube condenser of this invention, with its dual operating conditions, can simultaneously achieve heat exchange for different media through the arrangement of a first shell cavity and a second shell cavity, possessing dual-system processing capability and dual operating conditions. In the first operating condition, heat exchange occurs simultaneously between the media in the first and second shell cavities. When heat exchange is not required for the media in the second shell cavity, it can enter the second operating condition, in which heat exchange occurs only for the media in the first shell cavity, thereby reducing the coolant flow path and improving efficiency.

[0016] By combining a temperature probe, a first one-way valve, and an isolation pump assembly, this invention enables the utilization of the supply and return pipes in the second shell cavity under the second operating condition, thereby increasing the passive heat dissipation area and improving the condensation and cooling effect in the first shell cavity.

[0017] The isolation pump assembly of the present invention, through its structural design, can adapt to the rotation of the variable plate, and can achieve liquid drive and isolation effect simply by controlling the extension and retraction of the axial displacement shaft. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of the overall structure of the present invention.

[0019] Figure 2 This is a top view of the overall structure of the present invention.

[0020] Figure 3 for Figure 2 Cross-sectional view at point AA.

[0021] Figure 4 This is a partial cross-sectional view of the present invention.

[0022] Figure 5 for Figure 4 Enlarged schematic diagram of region A in the middle.

[0023] Figure 6 This is a three-dimensional half-sectional view of the present invention.

[0024] Figure 7 This is a three-dimensional half-sectional view of the variable displacement plate under the second operating condition of the present invention.

[0025] Figure 8 for Figure 7 Enlarged schematic diagram of region B in the middle.

[0026] Figure 9 This is a three-dimensional half-section view of the variable displacement plate under the first working condition of the present invention.

[0027] Figure 10 This is a schematic diagram of the variable speed control panel structure of the present invention.

[0028] Figure 11 This is a three-dimensional half-sectional view of the variable displacement disc of the present invention.

[0029] Figure 12 This is a schematic diagram of the structure of the connecting shell of the present invention.

[0030] In the diagram: 1. First cavity; 2. Second cavity; 3. Supply pipe; 4. Return pipe; 5. Docking clamp cavity; 6. Connecting shell; 7. Variable displacement disc; 8. Sealing ring; 701. Independent hole group; 702. Interconnecting hole group; 703. Interconnecting cavity; 704. Disc spindle; 705. Worm gear; 706. Worm section; 707. Drive shaft; 9. Temperature probe; 901. First check valve; 902. Column housing; 903. Integrated insert; 904. Second check valve; 905. First bypass hole; 906. Sealing rubber plug; 90 7. Pump plug structure; 908. Sealing top pipe; 909. Third one-way valve; 910. Second bypass hole; 911. First elastic element; 912. Limiting bracket; 913. Top shaft; 914. Second elastic element; 915. Limiting outer frame; 916. Inclined block; 917. Axial shifting shaft; 101. Diverter end cover; 102. Tube-side inlet pipe; 103. Tube-side pipe arrangement; 104. Separator layer; 105. Shell-side pipe arrangement; 106. Shell-side inlet pipe; 201. Rotating end cover; 918. One-way ball; 919. Compression spring element. Detailed Implementation

[0031] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0032] Please see Figures 1 to 12 This invention provides a technical solution: a dual-condition, dual-system shell-and-tube condenser. This invention aims to solve the problems of existing shell-and-tube condensers being unable to achieve dual-system processing and unable to adjust operating conditions according to the medium. Specific embodiments are as follows: Example 1: Please see Figure 1 and Figure 3 As shown, where Figure 1 The image shows the shape and connection of the first cavity 1 and the second cavity 2. Specifically, the first cavity 1 and the second cavity 2 are coaxially fixed by a flange.

[0033] Both the first cavity 1 and the second cavity 2 are equipped with a flow inlet pipe 3 and a return pipe 4, with several sets of each. A docking clamping cavity 5 is provided between the first cavity 1 and the second cavity 2. A connecting shell 6 is fixedly installed on the inner wall of the docking clamping cavity 5. There are four connecting shells 6 in total. The ends of the flow inlet pipe 3 and the return pipe 4 are individually connected to the connecting shells 6. The four connecting shells 6 are symmetrically distributed vertically and horizontally. (See reference here.) Figure 9 and Figure 12 As shown, the confluence shell 6 is used to connect and aggregate multiple flow pipes 3 or return pipes 4.

[0034] Please see Figure 3 A flow divider end cover 101 is fixedly installed at the end of the first cavity 1 via a flange. A partition layer 104 is provided inside the flow divider end cover 101, which divides the inner cavity of the flow divider end cover 101 into two parts. The upper part is connected to the flow supply pipe 3, and the lower part is connected to the return pipe 4. A pipe inlet pipe 102 and a pipe outlet pipe 103 are provided outside the flow divider end cover 101. The pipe inlet pipe 102 is connected to the upper part of the inner cavity of the flow divider end cover 101, and the pipe outlet pipe 103 is connected to the lower part of the inner cavity of the flow divider end cover 101.

[0035] Please see Figure 3 In this invention, shell-side pipe 105 and shell-side inlet pipe 106 are connected to the outside of both the first shell cavity 1 and the second shell cavity 2. The medium to be heat exchanged flows through the shell-side pipe 105 and the shell-side inlet pipe 106 respectively inside the first shell cavity 1 and the second shell cavity 2.

[0036] Please see Figure 3 In this invention, a rotating end cover 201 is fixedly installed at the end of the second cavity 2 via a flange. The rotating end cover 201 is a hemispherical shell. Figure 3 As shown in the example, the coolant in the flow pipe 3 in the second cavity 2 flows from left to right, enters the interior of the rotary end cover 201, and then returns to the return pipe 4, where it flows from right to left.

[0037] A transducer 7 is rotatably mounted between the connecting shell 6 and the transducer 7. A sealing ring 8 is provided on the surface of the connecting shell 6. The connecting shell 6 is in sealed contact with the transducer 7 through the sealing ring 8. The sealing ring 8 is as follows: Figure 12 As shown, a rubber ring is installed on the sealing ring 8, and the rubber ring contacts the variable plate 7 to achieve a sealing contact.

[0038] The operating conditions are switched by rotating the speed change panel 7. In the first operating condition, the flow pipe 3 in the first cavity 1 is directly connected to the flow pipe 3 in the second cavity 2 through the speed change panel 7, and at the same time, the return pipe 4 in the second cavity 2 is directly connected to the return pipe 4 in the first cavity 1 through the speed change panel 7. In the second operating condition, the flow pipe 3 in the first cavity 1 is directly connected to the return pipe 4 in the first cavity 1 through the speed change panel 7.

[0039] The surface of the variable dial 7 is provided with two independent hole groups 701, which are not connected to each other. In the first working condition, the flow pipe 3 in the first cavity 1 is connected to the flow pipe 3 in the second cavity 2 through one of the independent hole groups 701; the return pipe 4 in the second cavity 2 is connected to the return pipe 4 in the first cavity 1 through the other independent hole group 701.

[0040] The surface of the variable speed control panel 7 is provided with an interconnecting hole group 702. The interconnecting hole group 702 is open at one end facing the first housing cavity 1 and closed at the other end facing the second housing cavity 2. There are two interconnecting hole groups 702, and an interconnecting cavity 703 is provided between the two interconnecting hole groups 702 to achieve communication. In the second operating condition, the flow pipe 3 in the first cavity 1 is connected to the return pipe 4 in the first cavity 1 through the interconnection hole group 702 and the interconnection cavity 703.

[0041] A disc spindle 704 is fixedly installed at the center of the variable speed control disc 7. A worm gear 705 is fixedly installed on the disc spindle 704. A worm portion 706 is externally engaged with the worm gear 705. A drive shaft 707 is drivenly connected to the worm portion 706. One end of the drive shaft 707 extends to the outside of the second housing 2. The drive shaft 707 and the second housing 2 are sealed. The specific sealing method between the drive shaft 707 and the second housing 2 is a common structure in the prior art. Sealing packing, such as a rubber ring, can be used between the drive shaft 707 and the second housing 2 to achieve a seal.

[0042] The drive shaft 707 is precisely rotated via an external device, such as a servo motor.

[0043] Example 2: Based on Embodiment 1, a temperature probe 9 is further installed in the manifold housing 6, and the temperature probe 9 exists only in the manifold housing 6 connected to the return pipe 4. A first one-way valve 901 is installed at the closed end of one of the interconnecting hole groups 702, and an isolation pump assembly is provided at the closed end of the other interconnecting hole group 702.

[0044] The isolation pump assembly includes a cylindrical shell 902 fixedly mounted on the closed end of the interconnecting hole group 702. An integral embedded tube 903 is fixedly mounted on the cylindrical shell 902. A second one-way valve 904 is fixedly installed in the integral embedded tube 903. A first bypass hole 905 is opened on the integral embedded tube 903. The second one-way valve 904 communicates with the interior of the cylindrical shell 902 through the first bypass hole 905. The second one-way valve 904 is used to restrict the unidirectional flow of liquid into the cylindrical shell 902.

[0045] A sealing plug 906 is fixedly installed at one end of the integrated tube 903 inside the cylindrical shell 902. A pump plug structure 907 is installed inside the cylindrical shell 902. A sealing top tube 908 is fixedly installed on the pump plug structure 907. When the pump plug structure 907 moves into place in the direction of the sealing plug 906, the sealing plug 906 will press against the end of the sealing top tube 908 and seal the sealing top tube 908.

[0046] A third one-way valve 909 is fixedly installed in the sealing top tube 908. A second bypass hole 910 is connected to the end of the sealing top tube 908. The third one-way valve 909 is used to restrict the liquid in the column housing 902 from flowing unidirectionally into the second bypass hole 910. A first elastic element 911 is provided on the side of the pump plug structure 907 facing the sealing rubber plug 906; please refer to Figure 11 The first one-way valve 901 in this invention specifically includes a one-way ball 918 and a spring 919. The spring 919 applies pressure to the one-way ball 918, enabling the one-way ball 918 to unidirectionally seal the liquid. (Refer to reference...) Figure 4 and Figure 7 As shown, the first one-way valve 901 in this invention allows the coolant to flow unidirectionally from right to left. The second one-way valve 904 and the third one-way valve 909 in this invention have the same principle and structure as the first one-way valve 901, and will not be described again in this invention.

[0047] A drive assembly is provided on the side of the pump plug structure 907 away from the first elastic member 911. The drive assembly is used to control the axial movement of the pump plug structure 907 without affecting the rotation of the variable plate 7.

[0048] The drive assembly includes a limiting bracket 912 and a top shaft 913 that is inserted into the limiting bracket 912. The limiting bracket 912 is fixedly installed inside the connecting shell 6. A second elastic member 914 is provided on the outside of the top shaft 913. The second elastic member 914 causes the top shaft 913 to tend to move away from the pump plug structure 907. In the second operating condition, the pump plug structure 907 is coaxially aligned with the top shaft 913; A limiting frame 915 is fixedly installed on the limiting bracket 912. An inclined block 916 is installed in the limiting frame 915. An axial displacement shaft 917 is fixedly installed on the inclined block 916. One end of the axial displacement shaft 917 extends to the outside of the second shell cavity 2, and the axial displacement shaft 917 and the second shell cavity 2 are sealed. The axial displacement shaft 917 controls the lifting and lowering of the inclined block 916, so that the inclined block 916 squeezes and drives the top shaft 913. The axial displacement shaft 917 is axially driven by an external telescopic device, such as a cylinder or an electromagnetic telescopic device.

[0049] A control method for a dual-condition dual-system shell-and-tube condenser. The method uses a dual-condition dual-system shell-and-tube condenser. When heat exchange is performed on the medium in the first shell cavity 1 and the second shell cavity 2 at the same time, the feed pipe 3 in the first shell cavity 1 is directly connected to the feed pipe 3 in the second shell cavity 2 through the variable pressure plate 7. At the same time, the return pipe 4 in the second shell cavity 2 is directly connected to the return pipe 4 in the first shell cavity 1 through the variable pressure plate 7. When only the medium in the first cavity 1 is subjected to heat exchange, the variable pressure plate 7 is controlled to rotate so that the flow pipe 3 in the first cavity 1 is directly connected to the return pipe 4 in the first cavity 1 through the variable pressure plate 7.

[0050] In this invention, the coolant is input through the inlet pipe 102 and output through the outlet pipe 103. The coolant flows in the supply pipe 3 and the return pipe 4. Figure 3 Taking a medium-angle view as an example, the coolant in the supply pipe 3 flows from left to right, and the coolant in the return pipe 4 flows from right to left.

[0051] Under the first operating condition, there is medium flowing inside both the first cavity 1 and the second cavity 2. Under the first operating condition, the state of the variable displacement plate 7 is as follows: Figure 9 As shown in the diagram, at this time, the independent hole group 701 corresponds to the position of the sealing ring 8, so as to... Figure 9 Taking the medium-angle view as an example, the coolant in the left-side supply pipe 3 enters the right-side supply pipe 3 through the independent hole group 701, and the coolant in the right-side return pipe 4 enters the left-side return pipe 4 through the independent hole group 701, so that coolant flows in both the supply pipe 3 and the return pipe 4 inside the first cavity 1 and the second cavity 2. Under the first working condition, the medium inside the first cavity 1 and the second cavity 2 can simultaneously exchange heat with the coolant.

[0052] When the medium in the second cavity 2 does not require heat exchange, only the medium in the first cavity 1 undergoes heat exchange. The invention switches to the second operating condition, controlling the drive shaft 707 to rotate a fixed number of revolutions via an external device. This causes the worm gear 706 to drive the worm wheel 705 to rotate, which in turn drives the variable displacement disc 7 to rotate 90° via the disc shaft 704. After the variable displacement disc 7 rotates 90°, it enters the second operating condition. At this time, the state of the variable displacement disc 7 is as follows: Figure 7 As shown, the interconnecting hole group 702 corresponds to the sealing ring 8.

[0053] Similarly, Figure 7 Taking the medium-angle view as an example, the coolant in the left-side supply pipe 3 enters the inter-cavity 703 through the inter-hole group 702, and returns directly to the left-side return pipe 4 through the lower inter-hole group 702. This ensures that the coolant only flows in the corresponding supply pipe 3 and return pipe 4 in the first shell cavity 1, while the coolant stops flowing in the corresponding supply pipe 3 and return pipe 4 in the second shell cavity 2. This reduces the coolant flow path and lowers the system water volume. A smaller water volume means lower thermal inertia. When the heat load changes abruptly, the condenser outlet water temperature can change more quickly, the feedback delay of the automatic control system is shorter, and the system operation is more stable.

[0054] Taking the second embodiment as an example, the present invention, under the second operating condition, refers to... Figure 7 As shown, the present invention uses a temperature probe 9 to monitor the temperature of the coolant in the two connecting shells 6 located at the lower position. When the isolation pump assembly of the present invention is running, it can draw coolant from the interconnecting hole group 702 at the upper position and pump it under pressure into the supply pipe 3 corresponding to the second shell cavity 2. Under pressure, the coolant in the return pipe 4 corresponding to the second shell cavity 2 will return to the interconnecting hole group 702 at the lower position through the first one-way valve 901, so that the coolant in the supply pipe 3 and the return pipe 4 corresponding to the second shell cavity 2 will generate a controllable circulation flow.

[0055] In this embodiment of the invention, the coolant temperature input through the inlet pipe 102 is 20°C, and the medium temperature in the first cavity 1 is 100°C. When the coolant passes through the flow pipe 3 in the first cavity 1, it undergoes initial heat exchange with the medium in the first cavity 1, and its temperature rises to 50°C. (See reference...) Figure 4 As shown, under the second operating condition, the 50°C coolant flows directly into the return pipe 4 corresponding to the first shell cavity 1 through the interconnection cavity 703, undergoes heat exchange again, and is finally discharged through the tube-side manifold 103. At this time, the temperature of the coolant discharged from the tube-side manifold 103 rises to 70°C.

[0056] This invention can increase the passive heat dissipation area by utilizing the corresponding supply pipe 3 and return pipe 4 in the second shell cavity 2. Specifically, by operating the isolated pump assembly, coolant at 50°C is drawn from the interconnecting hole group 702 and pumped into the corresponding supply pipe 3 and return pipe 4 in the second shell cavity 2. Through the supply pipe 3 and return pipe 4 in the second shell cavity 2, the heat dissipation area is increased, achieving passive heat dissipation. The lower the operating rate of the isolated pump assembly, the longer the 50°C coolant stays in the supply pipe 3 and return pipe 4 in the second shell cavity 2, the longer the passive heat dissipation time, and the greater the temperature reduction. Temperature is monitored by the temperature probe 9. Figure 4 Taking the medium-angle view as an example, the temperature probe 9 on the left monitors the coolant temperature as Y, while the temperature probe 9 on the right monitors the coolant temperature as X. X is less than Y and is related to the operating rate of the isolation pump assembly. The slower the operating rate of the isolation pump assembly, the smaller X is. For example, if X is 35℃, it means that the coolant, driven by the isolation pump assembly, flows through the corresponding supply pipe 3 and return pipe 4 in the second shell cavity 2 and its temperature drops by 15℃ after passive heat dissipation.

[0057] Under pressure, the 35°C coolant enters the interconnection group 702 at the lower position through the first one-way valve 901, and mixes with the 50°C coolant that flows directly into the interconnection group 702 through the interconnection cavity 703. The temperature after mixing is Y, which is less than 50°C, thereby making the temperature of the coolant entering the return pipe 4 corresponding to the first shell cavity 1 even lower and improving the heat dissipation effect.

[0058] The isolated pump assembly of this invention, such as Figure 5 and Figure 7 As shown, the axial displacement shaft 917 is controlled by external settings to extend and retract. When the axial displacement shaft 917 reciprocates, the inclined block 916 can intermittently squeeze the top shaft 913, causing the top shaft 913 to move left and right. When the top shaft 913 moves to the left, it will squeeze the pump plug structure 907, driving the pump plug structure 907 to move to the left. When the top shaft 913 moves to the right, the pump plug structure 907 is reset under the elastic force of the first elastic member 911, so that the pump plug structure 907 exhibits reciprocating axial movement.

[0059] The pump plug structure 907 cooperates with the second check valve 904 and the third check valve 909 to draw coolant from the interconnecting hole group 702 and deliver it sequentially through the second check valve 904, the first bypass hole 905, the cylindrical shell 902, the third check valve 909, and the second bypass hole 910 to the corresponding delivery pipe 3 in the second shell cavity 2.

[0060] In the second operating condition, if passive heat dissipation is not required through the corresponding supply pipe 3 and return pipe 4 in the second shell cavity 2, the present invention only needs to control the axial displacement shaft 917 to move down to the position, so that the top shaft 913 moves to the left, driving the pump plug structure 907 to move to the left. When the pump plug structure 907 moves to the left, the sealing rubber plug 906 just blocks the end position of the sealing top pipe 908, so that the liquid in the column shell 902 cannot enter the third one-way valve 909, achieving a complete isolation effect.

[0061] Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A dual-condition, dual-system shell-and-tube condenser, comprising a first shell cavity and a second shell cavity, characterized in that: The first and second shell cavities are each provided with a flow inlet pipe and a return pipe, and a docking clamping cavity is provided between the first and second shell cavities; A manifold shell is fixedly installed on the inner wall of the docking cavity. There are four manifold shells in total. The ends of the flow pipe and the return pipe are respectively connected to the manifold shell individually. The four connecting shells are symmetrically distributed vertically and horizontally, and a variable speed plate is rotatably installed between the connecting shells. A sealing ring is provided on the surface of the connecting shell, and the connecting shell is in sealed contact with the variable speed plate through the sealing ring. The operating conditions are switched by rotating the speed change panel. In the first operating condition, the flow pipe in the first cavity is directly connected to the flow pipe in the second cavity through the speed change panel, and at the same time, the return pipe in the second cavity is directly connected to the return pipe in the first cavity through the speed change panel. In the second operating condition, the flow pipe in the first cavity is directly connected to the return pipe in the first cavity through the speed change panel. The surface of the variable speed control panel is provided with two independent sets of holes. In the first operating condition, the flow pipe in the first cavity is connected to the flow pipe in the second cavity through one of the independent sets of holes; the return pipe in the second cavity is connected to the return pipe in the first cavity through the other independent set of holes. The surface of the variable speed control panel is provided with a group of interconnecting holes. The end of the interconnecting hole group facing the first cavity is open and the end facing the second cavity is closed. There are two interconnecting hole groups, and an interconnecting cavity is provided between the two interconnecting hole groups to achieve communication. In the second operating condition, the flow pipe in the first shell cavity is connected to the return pipe in the first shell cavity through the interconnection hole group and the interconnection cavity.

2. The dual-condition dual-system shell-and-tube condenser according to claim 1, characterized in that: A disc spindle is fixedly installed at the center of the variable speed control disc, and a worm gear is fixedly installed on the disc spindle. A worm portion is meshed with the outside of the worm gear, and a drive shaft is drivenly connected to the worm portion. One end of the drive shaft extends to the outside of the second housing cavity, and the drive shaft and the second housing cavity are sealed.

3. The dual-condition dual-system shell-and-tube condenser according to claim 1, characterized in that: Temperature probes are installed in the manifold shells that are connected to the return pipe. A first check valve is installed at the closed end of one of the interconnecting hole groups, and a disconnected pumping assembly is installed at the closed end of the other interconnecting hole group.

4. The dual-condition dual-system shell-and-tube condenser according to claim 3, characterized in that: The isolation pump assembly includes a cylindrical shell fixedly mounted on the closed end of the interconnected hole group. An integral embedded tube is fixedly mounted on the cylindrical shell, and a second one-way valve is fixedly installed in the integral embedded tube. A first bypass hole is opened on the integral embedded tube, and the second one-way valve communicates with the interior of the cylindrical shell through the first bypass hole. The second one-way valve is used to restrict the liquid from flowing unidirectionally into the cylindrical shell.

5. The dual-condition dual-system shell-and-tube condenser according to claim 4, characterized in that: A sealing plug is fixedly installed at one end of the integrated tube inside the column shell. A pump plug structure is provided inside the column shell, and a sealing top tube is fixedly installed on the pump plug structure. When the pump plug structure moves into place in the direction of the sealing plug, the sealing plug will press against the end of the sealing top tube and seal the sealing top tube.

6. The dual-condition dual-system shell-and-tube condenser according to claim 5, characterized in that: A third one-way valve is fixedly installed in the sealed top tube, and a second winding hole is connected to the end of the sealed top tube. The third one-way valve is used to restrict the liquid in the column shell from flowing unidirectionally into the second winding hole. A first elastic element is provided on the side of the pump plug structure facing the sealing rubber plug. A drive assembly is provided on the side of the pump plug structure away from the first elastic element. The drive assembly is used to control the axial movement of the pump plug structure without affecting the rotation of the variable displacement plate.

7. The dual-condition dual-system shell-and-tube condenser according to claim 6, characterized in that: The drive assembly includes a limiting bracket and a top shaft that is inserted into the limiting bracket. The limiting bracket is fixedly installed inside the conduit shell. A second elastic element is provided on the outside of the top shaft, which causes the top shaft to tend to move away from the pump plug structure. In the second operating condition, the pump plug structure is coaxial with the top shaft; The limiting bracket is fixedly provided with a limiting outer frame, and a inclined block is limited and installed in the limiting outer frame. An axial displacement shaft is fixedly provided on the inclined block. One end of the axial displacement shaft extends to the outside of the second shell cavity, and the axial displacement shaft and the second shell cavity are sealed. The axial displacement shaft controls the lifting and lowering of the inclined block, so that the inclined block squeezes and drives the top shaft.

8. A method for controlling a dual-condition dual-system shell-and-tube condenser, the method employing the dual-condition dual-system shell-and-tube condenser as described in any one of claims 1-7, characterized in that: When the medium in the first cavity and the second cavity are subjected to heat exchange simultaneously, the flow pipe in the first cavity is directly connected to the flow pipe in the second cavity through the variable speed control panel, and the return pipe in the second cavity is directly connected to the return pipe in the first cavity through the variable speed control panel. When only the medium in the first cavity is subjected to heat exchange, the variable displacement plate is rotated so that the supply pipe in the first cavity is directly connected to the return pipe in the first cavity through the variable displacement plate.

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