Double-pipe heat exchanger and heat pump equipment

Abstract

The utility model discloses a double-pipe heat exchanger and heat pump equipment, and the double-pipe heat exchanger comprises an inner pipe and an outer pipe; the inner pipe comprises an inlet pipe section, a heat exchange pipe section and a discharge pipe section, a secondary refrigerant inlet of the inlet pipe section and a secondary refrigerant outlet of the discharge pipe section are both communicated with a pipeline of heat pump equipment, the outer pipe is arranged outside the heat exchange pipe section in a sleeving mode, and the inner wall of the outer pipe and the outside of the heat exchange pipe section are matched to form a refrigerating channel for refrigerant flowing; an inlet close to the secondary refrigerant inlet is formed in one end of the outer pipe, an outlet close to the secondary refrigerant outlet is formed in the other end of the outer pipe, and the inlet and the outlet are both communicated with a refrigerating system of the heat pump equipment; the outer pipe and the heat exchange pipe section are both arranged in a spiral shape, a disturbance part is arranged outside the heat exchange pipe section, the disturbance part is distributed along the extending path of the heat exchange pipe section, and the disturbance part is used for disturbing refrigerants. By means of the arrangement, the problem that the double-pipe heat exchanger cannot provide good heat exchange efficiency in the environment with large fluid flow is effectively solved.

Description

Technical Field

[0001] The utility model relates to the technical field of heat exchangers, in particular to a shell and tube heat exchanger and a heat pump device. Background Art

[0002] Currently, the shell-and-tube heat exchangers used in heat pump systems typically consist of a copper tube and an outer tube. The outer tube is encased in a copper tube, with water flowing inside and the refrigerant flowing outside. While this type of heat exchanger offers excellent heat transfer efficiency, it is typically only suitable for environments with low water flow rates. In environments with high water flow rates, this type of heat exchanger cannot provide adequate heat transfer, resulting in a significant difference between the inlet and outlet water temperatures, impacting the overall energy efficiency of the heat pump. Utility Model Content

[0003] The utility model mainly provides a shell and tube heat exchanger to solve the problem that the shell and tube heat exchanger cannot provide good heat exchange efficiency in an environment with large fluid flow.

[0004] To achieve the above-mentioned purpose, the present invention proposes a double-tube heat exchanger, which includes an inner tube and an outer tube; wherein,

[0005] The inner tube includes an inlet tube section, a heat exchange tube section, and a discharge tube section. The coolant inlet of the inlet tube section and the coolant outlet of the discharge tube section are both connected to the pipeline of the heat pump equipment. The outer tube is sleeved on the outside of the heat exchange tube section. The inner wall of the outer tube cooperates with the outside of the heat exchange tube section to form a refrigeration channel for the flow of refrigerant.

[0006] One end of the outer tube is provided with an inlet arranged close to the brine inlet, and the other end is provided with an outlet arranged close to the brine outlet, and both the inlet and the outlet are connected to the refrigeration system of the heat pump equipment;

[0007] The outer tube and the heat exchange tube section are both arranged in a spiral shape. A disturbance portion is provided on the outside of the heat exchange tube section. The disturbance portion is distributed along the extension path of the heat exchange tube section and is used to disturb the refrigerant.

[0008] In some embodiments of the present invention, there are at least two heat exchange tube segments, at least two of the heat exchange tube segments are intertwined with each other, and the disturbance portion is formed between the at least two heat exchange tube segments.

[0009] In some embodiments of the present invention, the heat exchange pipe segment includes a heat exchange pipe segment body and a spiral body, the spiral body is sleeved on the outside of the heat exchange pipe segment body, and the disturbance portion is formed on the spiral body.

[0010] In some embodiments of the present invention, a plurality of spiral protrusions are formed on the outside of the heat exchange tube segment, and the plurality of spiral protrusions are distributed along the extension path of the heat exchange tube segment, and the disturbance portion is formed on each of the spiral protrusions.

[0011] In some embodiments of the present invention, the spacing between the multiple spiral protrusions is 0.5-5 mm.

[0012] In some embodiments of the present invention, the height of the plurality of spiral protrusions is 0.2-1 mm.

[0013] In some embodiments of the present invention, the inner tube is made of titanium, the outer tube is made of steel, the wall thickness of the inner tube is 0.5-0.6 mm, and the diameter of the inner tube is 15-22 mm.

[0014] In some embodiments of the present invention, the shell and tube heat exchanger also includes a bypass assembly, the bypass assembly includes a flow guide, one end of the flow guide is connected to the inlet pipe section pipeline, and the other end is connected to the outlet pipe section pipeline, and the flow guide is used to mix the refrigerant in the inlet pipe section with the refrigerant in the outlet pipe section.

[0015] In some embodiments of the present invention, the bypass assembly further includes a control valve, which is disposed on the flow guide member and is used to control the flow rate of the refrigerant in the flow guide member.

[0016] To achieve the above-mentioned purpose, the present invention further provides a heat pump device, which includes a shell and tube heat exchanger.

[0017] The beneficial effects of the present invention are as follows: different from the prior art, the shell and tube heat exchanger disclosed in the present invention transports refrigerant in the refrigeration channel and transports coolant in the inner tube, and heat exchange is performed in a manner that the refrigerant wraps the inner tube, and a disturbance portion is provided on the outside of the heat exchange tube section, which can effectively disturb the refrigerant so that the refrigerant can form multiple longitudinal vortices in the refrigeration channel, thereby increasing the heat exchange rate between the refrigerant and the coolant in the inner tube, thereby greatly improving the heat exchange between the refrigerant and the coolant in the inner tube, thereby enhancing the heat exchange effect, and even in an environment with a large fluid flow rate, the temperature difference between the inlet temperature and the discharge temperature of the coolant can be well controlled, thereby improving the heat exchange efficiency of the shell and tube heat exchanger and improving the energy efficiency of the heat pump equipment. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying any creative work.

[0019] Figure 1 This is a structural diagram of an embodiment of a double-tube heat exchanger of the utility model;

[0020] Figure 2 This is a schematic diagram of the cross-sectional structure of an embodiment of the outer tube and heat exchange tube section of the utility model;

[0021] Figure 3 This is a structural diagram of an embodiment of a heat exchange tube segment according to the present invention;

[0022] Figure 4 This is a schematic cross-sectional view of another embodiment of the outer tube and heat exchange tube section of the utility model;

[0023] Figure 5 This is a structural schematic diagram of another embodiment of the heat exchange tube segment of the utility model;

[0024] Figure 6 This is a schematic cross-sectional view of another embodiment of the outer tube and heat exchange tube section of the utility model;

[0025] Figure 7 This is a structural schematic diagram of another embodiment of the heat exchange tube segment of the utility model.

[0026] Description of Figure Numbers:

[0027] 1. Inner tube; 11. Inlet tube section; 12. Outlet tube section; 13. Disturbance section; 14. Heat exchange tube section; 14a. Heat exchange tube section body; 14b. Helix; 14c. Spiral protrusion; 2. Outer tube; 21. Wrapped tube section; 22. First joint; 221. Inlet; 23. Second joint; 231. Outlet; 24. Refrigeration channel; 3. Bypass assembly; 31. Flow guide; 32. Control valve.

[0028] The realization of the purpose, functional features and advantages of the present invention will be further explained in conjunction with embodiments and with reference to the accompanying drawings. DETAILED DESCRIPTION

[0029] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0030] In this utility model, unless otherwise specified or limited, the terms "connection" and "fixation" should be understood in a broad sense. For example, "fixation" can mean fixed connection, detachable connection, or integration; mechanical connection or electrical connection; direct connection or indirect connection through an intermediate medium; internal communication between two elements or interaction between two elements, unless otherwise specified. For those skilled in the art, the specific meanings of the above terms in this utility model can be understood according to specific circumstances.

[0031] In addition, in this utility model, the descriptions of "first" and "second" are for descriptive purposes only and should not be understood as indicating or implying their relative importance or implicitly indicating the number of the technical features indicated. Therefore, the features specified as "first" and "second" may explicitly or implicitly include at least one of such features. In addition, the technical solutions between the various embodiments can be combined with each other, but this must be based on the fact that they can be implemented by ordinary technicians in this field. When the combination of technical solutions is mutually contradictory or cannot be implemented, it should be deemed that such combination of technical solutions does not exist and is not within the scope of protection required by this utility model.

[0032] The utility model proposes a shell and tube heat exchanger, referring to Figure 1 and Figure 2 The shell and tube heat exchanger includes an inner tube 11 and an outer tube 2; wherein, the inner tube 1 includes an inlet pipe section 11, a heat exchange pipe section 14 and a discharge pipe section 12, the refrigerant inlet of the inlet pipe section 11 and the refrigerant outlet of the discharge pipe section 12 are both connected to the pipeline of the heat pump equipment, and the outer tube 2 is sleeved on the outside of the heat exchange pipe section 14, and the inner wall of the outer tube 2 and the outside of the heat exchange pipe section 14 cooperate to form a refrigeration channel 24 for the flow of refrigerant.

[0033] One end of the outer tube 2 is provided with an inlet 221, located near the brine inlet, and the other end is provided with an outlet 231, located near the brine outlet. Both inlet 221 and outlet 231 are connected to the refrigeration system of the heat pump equipment. The outer tube 2 and the heat exchange tube segment 14 are both arranged in a spiral shape. The heat exchange tube segment 14 is provided with a disturbance portion 13 on its exterior, distributed along the extension path of the heat exchange tube segment 14, and is used to disturb the refrigerant.

[0034] Based on the above-mentioned scheme, the shell and tube heat exchanger transports refrigerant in the refrigeration channel 24 and transports the coolant in the inner tube 1, and heat exchange is performed in a manner that the refrigerant wraps the inner tube 1, and a disturbance portion 13 is provided on the outside of the heat exchange tube section 14. The disturbance portion 13 can effectively disturb the refrigerant so that the refrigerant can form multiple longitudinal vortices in the refrigeration channel 24, thereby increasing the heat exchange rate between the refrigerant and the coolant in the inner tube 1. This can greatly improve the heat exchange between the refrigerant and the coolant in the inner tube 1, thereby enhancing the heat exchange effect. In this way, even in an environment with a large fluid flow rate, the temperature difference between the inlet temperature and the discharge temperature of the coolant can be well controlled, thereby improving the heat exchange efficiency of the shell and tube heat exchanger and improving the energy efficiency of the heat pump equipment.

[0035] It's understood that both the outer tube and the heat exchange tube section are arranged in a spiral configuration. That is, the outer tube and the inner tube section located within the outer tube are spirally stacked together, forming a spiral path that helps increase heat exchange effectiveness and efficiency. Of the inner and outer tubes, only the outer circumference of the inner tube has a threaded structure, which turbulently stirs the refrigerant within the cooling channel, enhancing the heat exchange efficiency and effectiveness of the double-tube heat exchanger.

[0036] The refrigerant may be difluoromethane (R32), propane (R290), carbon dioxide (R744), 1,1,1,2-tetrafluoroethane (R134A), pentafluoropropane (R2345FA), a new hydrofluorocarbon refrigerant (R515B), or a mixed refrigerant (R410A) composed of 50% by mass of difluoromethane and 50% by mass of pentafluoroethane (R125). The secondary refrigerant may be water or brine.

[0037] like Figure 2 and Figure 3 As shown, there are at least two heat exchange tube segments 14, which are intertwined with each other, and a disturbance portion 13 is formed between the at least two heat exchange tube segments 14. This arrangement ensures the flow rate of the brine in the inner tube 1, and further increases the disturbance of the refrigerant by forming the disturbance portion 13 by the at least two inner tubes 1 being intertwined, thereby further improving the heat exchange efficiency between the refrigerant and the brine in the inner tube 1.

[0038] Specifically, the disturbance portion 13 may be a gap between the heat exchange tube segments 14 .

[0039] In the embodiment of the present application, there are three heat exchange tube segments 14 , and the three heat exchange tube segments 14 are intertwined with each other.

[0040] like Figure 4 and Figure 5As shown, the heat exchange tube segment 14 includes a heat exchange tube segment 14 body and a spiral 14b. The spiral 14b is sleeved on the exterior of the heat exchange tube segment 14 body, and the disturbance portion 13 is formed on the spiral 14b. The spiral 14b can be a long spring. The long spring forms a spiral structure on the outer peripheral wall of the heat exchange tube segment 14 body, increasing the spirality of the outer peripheral wall of the heat exchange tube segment 14 body. This arrangement not only quickly forms the spiral structure of the heat exchange tube segment 14 body, facilitating processing and assembly, but also creates a disturbance in the refrigerant within the refrigeration channel 24. This can significantly improve the heat exchange efficiency and effect between the refrigerant and the brine in the inner tube 1 when the fluid flow rate is high.

[0041] like Figure 6 and Figure 7 As shown, a plurality of spiral protrusions 14 c are formed on the outside of the heat exchange tube section 14 . The plurality of spiral protrusions 14 c are distributed along the extension path of the heat exchange tube section 14 , and the disturbance portion 13 is formed on each spiral protrusion 14 c.

[0042] Through the spiral protrusion 14c, the refrigerant can form multiple longitudinal vortices in the refrigeration channel 24, increasing the heat exchange rate between the refrigerant and the inner tube 1, which can greatly improve the heat exchange between the refrigerant and the coolant in the inner tube 1, thereby enhancing the heat exchange effect.

[0043] The spacing between the plurality of spiral protrusions 14c is 0.5-5 mm. The protrusion height of the plurality of spiral protrusions 14c is 0.2-1 mm. When the height of the spiral protrusions 14c is small, the spacing between the spiral protrusions 14c is small. Similarly, when the height of the spiral protrusions 14c is large, the spacing between the spiral protrusions 14c is large.

[0044] For example, the protrusion height of the spiral protrusion 14c is 0.2mm, and the spacing between multiple spiral protrusions 14c is 5mm; the protrusion height of the spiral protrusion 14c is 0.6mm, and the spacing between multiple spiral protrusions 14c is 2.5mm; the protrusion height of the spiral protrusion 14c is 1mm, and the spacing between multiple spiral protrusions 14c is 0.5mm.

[0045] Such a configuration limits the height and spacing of the spiral protrusions 14c, so as to better disturb the refrigerant, thereby improving the heat exchange efficiency between the refrigerant and the coolant in the inner tube 1, thereby improving the heat exchange effect and efficiency of the shell-and-tube heat exchanger.

[0046] In an embodiment of the present application, the number of the multiple spiral protrusions 14c can be set to four, and the four spiral protrusions 14c are all spirally distributed along the extension path of the inner tube 1. When the refrigerant flow rate in the inner tube 1 is large, the four spiral protrusions 14c can be particularly effective in improving the heat exchange efficiency and effect between the refrigerant and the inner tube 1.

[0047] The inner tube 1 is made of titanium, and the outer tube 2 is made of steel. The wall thickness of the inner tube 1 is 0.5-0.6 mm, and the diameter of the inner tube 1 is 15-22 mm. This configuration can enhance the overall structural performance of the double-tube heat exchanger, improve the pressure bearing performance, and ensure stability during use.

[0048] The wall thickness of the inner tube 11 is 0.5-0.6 mm. For example, the wall thickness of the inner tube 11 can be 0.5 mm or 0.6 mm. Since the heat exchange tube section 14 is wound into a spiral shape, limiting the wall thickness of the inner tube 11 to 0.5-0.6 mm facilitates the pressing of the heat exchange tube section 14 into the spiral shape, effectively prevents brittle fracture of the titanium inner tube 11, and reduces costs.

[0049] The diameter of the inner tube 11 is 15-22 mm. For example, the diameter of the inner tube 11 can be 15 mm, 15.88 mm, 19.05 mm, or 22 mm. By limiting the diameter of the inner tube 11 to 15-22 mm, the diameter of the titanium tube is increased to a certain extent compared to the diameter of traditional titanium tubes, thereby reducing the resistance of the refrigerant and improving the performance of the double-tube heat exchanger.

[0050] Reference Figure 1 The shell and tube heat exchanger also includes a bypass component 3, which includes a flow guide 31. One end of the flow guide 31 is connected to the pipeline entering the pipe section 11, and the other end is connected to the pipeline exiting the pipe section 12. The flow guide 31 is used to mix the refrigerant in the entering pipe section 11 with the refrigerant in the discharge pipe section 12.

[0051] A flow guide 31 is provided between the inlet pipe section 11 and the outlet pipe section 12, so that the refrigerant entering the pipe section 11 can be partially diverted into the outlet pipe section 12 and mixed with the refrigerant in the outlet pipe section 12. This can effectively reduce the impact on the performance of the heat exchange pipe section close to the refrigerant side. In this way, even in an environment with a large fluid flow rate, the temperature difference between the inlet temperature and the discharge temperature of the refrigerant can be further controlled, thereby improving the heat exchange efficiency of the condensing side of the shell and tube heat exchanger and improving the energy efficiency of the heat pump equipment.

[0052] The bypass assembly 3 further includes a control valve 32 , which is disposed on the flow guide 31 . The control valve 32 is used to control the flow of the coolant in the flow guide 31 .

[0053] With such a configuration, the flow rate of the refrigerant entering the pipe section 11 and flowing to the discharge pipe section 12 is controlled by the control valve 32, so that the discharge temperature can be controlled to obtain different refrigerant discharge temperatures. It is easier to control the refrigerant temperature during discharge, so as to adjust the discharge temperature according to different application scenarios and improve the performance of the shell and tube heat exchanger.

[0054] The control valve 32 is a one-way control valve 32 that is used to restrict the brine in the flow guide 31 from flowing from the inlet pipe section 11 to the outlet pipe section 12. When the brine entering the pipe section 11 is diverted to the outlet pipe section 12 for mixing, only the brine entering the pipe section 11 is allowed to flow to the outlet pipe section 12, effectively preventing the brine from the outlet pipe section 12 from flowing to the inlet pipe section 11, thereby avoiding affecting the brine discharge temperature and ensuring the stability of the heat exchange efficiency of the double-tube heat exchanger.

[0055] At the same time, it can also prevent the coolant in the guide member 31 from flowing back to the inlet pipe section 11, which can reduce the impact on the coolant discharge temperature, thereby ensuring the stability of the heat exchange efficiency of the shell and tube heat exchanger.

[0056] The control valve 32 may be a one-way solenoid valve or a one-way throttle valve, and is not specifically limited here as long as it can control the brine flow of the guide member 31 .

[0057] In some embodiments, the flow guide 31 may be a titanium tube, which has excellent corrosion resistance. This allows the coolant entering the pipe section 11 to be stably directed to the discharge pipe section 12, achieving mixing and controlling the coolant discharge temperature. This also helps extend the service life of the double-tube heat exchanger.

[0058] In other embodiments, the flow guide 31 can also be a rubber hose. The rubber hose has a low cost and can greatly reduce production costs and improve the practicality of the shell and tube heat exchanger while ensuring that the refrigerant entering the pipe section 11 is mixed with the refrigerant exiting the pipe section 12.

[0059] The heat exchange tube section and the outer tube 2 are both arranged in a spiral shape. Such an arrangement can increase the heat exchange process of the shell and tube heat exchanger and improve the heat exchange efficiency of the shell and tube heat exchanger.

[0060] Reference Figure 1 The outer tube 2 includes a wrapping tube section 21, a first joint 22, and a second joint 23. The first joint 22 is located near the inlet tube section 11, and the second joint 23 is located near the outlet tube section 12. One end of the wrapping tube section 21 is sealed to the first joint 22, and the other end is sealed to the second joint 23. The first joint 22 is also sealed to the outside of the inlet tube section 11, and the second joint 23 is also sealed to the outside of the outlet tube section 12. The inlet 221 is formed in the first joint 22, and the outlet 231 is formed in the second joint 23. This facilitates both assembly of the shell and tube heat exchanger and subsequent maintenance of the shell and tube heat exchanger.

[0061] The present invention also provides a heat pump device including a double-tube heat exchanger. The heat pump device can be used in swimming pools or in aquaculture, for example, fish farming, where the device has a wide water temperature adjustment range and a heat pump device using a double-tube heat exchanger is more suitable.

[0062] The specific structure of the shell and tube heat exchanger refers to the above embodiments. Since the heat pump equipment adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought by the technical solutions of the above embodiments, which will not be described one by one here.

[0063] The above description is merely an optional embodiment of the present invention and does not limit the patent scope of the present invention. All equivalent structural transformations made by utilizing the contents of the present invention specification and drawings under the inventive concept of the present invention, or direct / indirect application in other related technical fields are included in the patent protection scope of the present invention.

Claims

1. A double-tube heat exchanger, used in heat pump equipment, characterized in that: The double-tube heat exchanger includes an inner tube and an outer tube; wherein, The inner tube includes an inlet tube section, a heat exchange tube section, and a discharge tube section. The coolant inlet of the inlet tube section and the coolant outlet of the discharge tube section are both connected to the pipeline of the heat pump equipment. The outer tube is sleeved on the outside of the heat exchange tube section. The inner wall of the outer tube cooperates with the outside of the heat exchange tube section to form a refrigeration channel for the flow of refrigerant. One end of the outer tube is provided with an inlet arranged close to the brine inlet, and the other end is provided with an outlet arranged close to the brine outlet, and both the inlet and the outlet are connected to the refrigeration system of the heat pump equipment; The outer tube and the heat exchange tube section are both arranged in a spiral shape. A disturbance portion is provided on the outside of the heat exchange tube section. The disturbance portion is distributed along the extension path of the heat exchange tube section and is used to disturb the refrigerant.

2. The double-tube heat exchanger according to claim 1, characterized in that: There are at least two heat exchange tube sections, and the at least two heat exchange tube sections are intertwined with each other. The disturbance portion is formed between the at least two heat exchange tube sections.

3. The double-tube heat exchanger according to claim 1, characterized in that: The heat exchange pipe segment includes a heat exchange pipe segment body and a spiral body. The spiral body is sleeved on the outside of the heat exchange pipe segment body, and the disturbance part is formed on the spiral body.

4. The double-tube heat exchanger according to claim 1, characterized in that: A plurality of spiral protrusions are formed on the outside of the heat exchange tube section. The plurality of spiral protrusions are distributed along the extension path of the heat exchange tube section. The disturbance portion is formed on each of the spiral protrusions.

5. The double-tube heat exchanger according to claim 4, characterized in that: The spacing between the multiple spiral protrusions is 0.5-5 mm.

6. The double-tube heat exchanger according to claim 4, characterized in that: The protrusion height of the multiple spiral protrusions is 0.2-1 mm.

7. The double-tube heat exchanger according to claim 1, characterized in that: The inner tube is made of titanium, the outer tube is made of steel, the wall thickness of the inner tube is 0.5-0.6 mm, and the diameter of the inner tube is 15-22 mm.

8. The double-tube heat exchanger according to claim 1, characterized in that: The shell and tube heat exchanger also includes a bypass assembly, which includes a flow guide. One end of the flow guide is connected to the inlet pipe section pipeline, and the other end is connected to the outlet pipe section pipeline. The flow guide is used to mix the refrigerant in the inlet pipe section with the refrigerant in the outlet pipe section.

9. The double-tube heat exchanger according to claim 8, characterized in that: The bypass assembly further includes a control valve, which is disposed on the flow guide and is used to control the flow of the coolant in the flow guide.

10. A heat pump device, characterized in that: The heat pump device comprises the double-tube heat exchanger according to any one of claims 1 to 9.

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