Heat pipe condenser desuperheating system, refrigeration system, air conditioner and desuperheating method

Abstract

The present invention discloses a heat pipe condenser desuperheating system, a refrigeration system, an air conditioner, and a desuperheating method. The heat pipe condenser desuperheating system includes: a condenser including a condensing portion; a compressor connected to the condensing portion; an evaporator including an evaporating portion connected to the compressor for evaporating a refrigerant and outputting it to the compressor for compression; a heat pipe assembly including an evaporating section and a condensing section connected to the evaporating section; a cooling medium circulated between the evaporating section and the condensing section; the evaporating section is provided between the condensing portion and the compressor to heat exchange the compressed refrigerant output by the compressor with the cooling medium in the evaporating section before entering the condensing portion; and the condensing section is provided between the evaporating section and the compressor to heat exchange the evaporated refrigerant output by the evaporating section with the cooling medium in the condensing section before entering the compressor. The object of the present invention is to provide a heat pipe condenser desuperheating system that can improve the heat exchange efficiency of the condenser and improve the overall heat exchange performance.

Description

Technical Field

[0001] The present invention relates to the technical field of air conditioning and refrigeration, and in particular to a heat pipe condenser desuperheating system, a refrigeration system, an air conditioner and a desuperheating method. Background Art

[0002] With the advancement of the green and efficient refrigeration action plan, high-efficiency and energy-saving equipment will become the mainstream choice in the market. In refrigeration systems such as chillers, the heat exchanger is the "heart" of the system's heat exchange, and its heat transfer performance seriously affects the heat transfer efficiency of the heat exchanger.

[0003] In an actual refrigeration cycle, the high-temperature, high-pressure gaseous refrigerant discharged from the compressor is in a superheated state, meaning that the refrigerant vapor entering the condenser is in a superheated state. There is a transition point temperature at which the superheated gaseous refrigerant undergoes phase change. When the temperature of the superheated gaseous refrigerant is higher than the transition point, the refrigerant vapor releases sensible heat without undergoing a phase change. However, when the temperature of the gaseous refrigerant is lower than the transition point, the vapor releases latent heat and condenses. Therefore, in the condenser, the process by which the condenser tube condenses the superheated refrigerant vapor into a subcooled liquid refrigerant includes: 1. Cooling the superheated vapor to saturated vapor; 2. Condensing the saturated vapor into a saturated liquid refrigerant; and 3. Cooling the saturated liquid refrigerant to a subcooled liquid refrigerant. Processes 1 and 3 above represent single-phase heat transfer, while process 2 represents phase change heat transfer. This means that actual operation involves both single-phase and phase change heat transfer processes. Therefore, there must be a superheated gas cooling area inside the condenser where no phase change occurs (that is, the area where process 1 occurs). It is estimated that the heat exchange of superheated gas cooling (process 1) in the existing shell and tube condenser accounts for about 4-10% of the total heat exchange. However, since the heat transfer coefficient of the gas non-phase change area is much lower than that of the phase change area, the proportion of the non-phase change (process 1) heat exchange area in the total area is as high as 15-40%. That is, due to the low heat transfer coefficient of process 1, more heat exchange area is occupied, resulting in a low effective utilization rate of the area of ​​the entire tube bundle.

[0004] Currently, the enhancement of high-efficiency tubes is based on the concept of phase change enhanced heat transfer, specifically how to enhance the film condensation heat transfer efficiency in process 2. For example, this can be achieved through integrated internal and external extrusion molding, forming a spiral three-dimensional fin structure on the outside, and other methods to improve heat transfer efficiency. This type of heat exchange tube has a small fin pitch and low fin height, making the condensation heat transfer in the phase change zone (process 2) very efficient, but the effect is very poor in the superheated gas cooling zone (process 1). Because the entire condensing tube bundle often uses a uniform tube shape, the heat transfer area of ​​the entire tube bundle is not fully utilized (there is an inefficient superheat cooling zone). Summary of the Invention

[0005] The object of the present invention is to provide a heat pipe condenser desuperheating system that can improve the heat exchange efficiency of the condenser and improve the overall heat exchange performance, and a refrigeration system, air conditioner and desuperheating method using the heat pipe condenser desuperheating system.

[0006] The present invention discloses a heat pipe condenser desuperheating system, comprising:

[0007] The condenser includes a condensing portion for condensing the refrigerant;

[0008] a compressor connected to the condensing unit, configured to compress the refrigerant and then output the refrigerant to the condensing unit for condensation;

[0009] An evaporator, comprising an evaporation portion connected to the compressor, for evaporating the refrigerant and outputting it to the compressor for compression;

[0010] A heat pipe assembly includes an evaporation section and a condensation section connected to the evaporation section. A cooling medium circulates between the evaporation section and the condensation section. The evaporation section is arranged between the condensation section and the compressor to exchange heat between the compressed refrigerant output by the compressor and the cooling medium in the evaporation section before entering the condensation section. The condensation section is arranged between the evaporation section and the compressor to exchange heat between the evaporated refrigerant output by the evaporation section and the cooling medium in the condensation section before entering the compressor.

[0011] In some embodiments, the condensing section includes one or more condensing section tube cores for heat exchange between the evaporated refrigerant output from the evaporating portion and the cooling medium, and the outer surface of the condensing section tube core is provided with a porous structure for heat exchange of the refrigerant.

[0012] In some embodiments, the porous structure includes a plurality of concave holes arranged around the circumference of the condensing section tube core, and the plurality of concave holes are evenly arranged.

[0013] In some embodiments, the evaporation section includes an evaporation section tube core, and the condensation section includes a condensation section tube core. The length of the condensation section tube core is smaller than the length of the evaporation section tube core.

[0014] In some embodiments, the evaporation section includes one or more evaporation section tube cores for heat exchange between the compressed refrigerant output by the compressor and the cooling medium, and the condensation section includes one or more condensation section tube cores for heat exchange between the evaporated refrigerant output by the evaporation section and the cooling medium. The evaporation section tube core and / or the inner tube wall of the condensation section tube core are provided with a plurality of strip grooves distributed along the circumferential direction, and the strip grooves extend axially along the inner tube wall to provide capillary force when the cooling medium flows back from the condensation section to the evaporation section.

[0015] In some embodiments, the evaporation section includes one or more evaporation section tube cores for heat exchange between the compressed refrigerant output by the compressor and the cooling medium. The outer surface of the evaporation section tube core is a smooth surface. The evaporation section also includes fins arranged around the outer surface of the evaporation section tube core. The fins are flat wings, corrugated wings or windowed wings.

[0016] In some embodiments, the evaporation section includes a plurality of evaporation section tube cores for heat exchange between the compressed refrigerant output by the compressor and the cooling medium, the condensation section includes a plurality of condensation section tube cores for heat exchange between the evaporated refrigerant output by the evaporation section and the cooling medium, and the heat pipe assembly also includes an insulating tube with both ends respectively connecting the plurality of evaporation section tube cores and the plurality of condensation section tube cores.

[0017] In some embodiments, the one insulated tube and the multiple evaporation section tube cores and the multiple condensation section tube cores connected at both ends thereof form a heat pipe layer, and the heat pipe assembly includes multiple stacked heat pipe layers.

[0018] In some embodiments, the condenser includes a first cylinder, the condensation part and the evaporation section are both arranged in the first cylinder, the first cylinder is provided with an air inlet connected to the compressor for receiving the refrigerant output by the compressor, and the evaporation section is located between the air inlet and the condensation part.

[0019] In some embodiments, the first cylinder further includes a first support plate that supports the evaporation section and is arranged between the evaporation section and the condensation section. The first support plate is provided with a first elongated hole extending along the axial direction of the first cylinder and ribs connecting the two ends of the first elongated hole along the length direction.

[0020] In some embodiments, the first cylinder is further provided with a cooling water inlet and a cooling water outlet connected to the condensation section, and the cooling water inlet and the cooling water outlet are respectively used to introduce cooling water for condensing the refrigerant into the condensation section and output the cooling water after condensing the refrigerant in the condensation section.

[0021] In some embodiments, the evaporator includes a second cylinder, the evaporation section and the condensation section are both arranged in the second cylinder, and the second cylinder is provided with an outlet connected to the compressor for outputting the evaporated refrigerant to the compressor, and the condensation section is located between the outlet and the evaporation section.

[0022] In some embodiments, the second cylinder further includes a second support plate that supports the condensation section and is arranged between the condensation section and the evaporation section. The second support plate is provided with a second elongated hole extending along the axial direction of the second cylinder and a transverse support plate connecting the two ends of the elongated hole along the width direction.

[0023] In some embodiments, the second cylinder is further provided with a chilled water inlet and a chilled water outlet connected to the evaporation part, and the chilled water inlet and the chilled water outlet are respectively used to input liquid water for evaporating the refrigerant into the evaporation part and output liquid water after the refrigerant evaporates in the evaporation part.

[0024] A second aspect of the present invention discloses a refrigeration system, comprising the heat pipe condenser desuperheating system.

[0025] A third aspect of the present invention discloses an air conditioner comprising the refrigeration system.

[0026] A fourth aspect of the present invention discloses a desuperheating method using the heat pipe condenser desuperheating system, comprising:

[0027] Before the compressed refrigerant output by the compressor enters the condensation section, the cooling medium exchanges heat with the refrigerant in the evaporation section, so that the refrigerant is cooled to a saturated vapor state before entering the condensation section;

[0028] After the cooling medium completes heat exchange with the refrigerant in the evaporation section, it enters the condensation section to exchange heat with the evaporated refrigerant output from the evaporation section, so that the evaporated refrigerant output from the evaporation section evaporates the liquid refrigerant into gas before entering the compressor;

[0029] The cooling medium returns to the evaporation section after completing heat exchange with the refrigerant in the condensation section.

[0030] The heat pipe condenser desuperheating system provided by the present invention is configured by disposing an evaporation section of a heat pipe assembly between the condensing portion of the condenser and the compressor, and a condensation section of a heat pipe assembly between the evaporating portion of the evaporator and the compressor. The heat pipe assembly is used to cool the refrigerant before it enters the condensing portion, converting it into a saturated vapor state. This significantly improves the heat exchange efficiency of the refrigerant in the condenser after the conversion, thereby simplifying the condenser structure. Simultaneously, the heat pipe assembly can efficiently transfer the heat absorbed by the evaporation section to the evaporator, and this heat is used to heat the refrigerant output from the evaporation portion of the evaporator, thereby evaporating droplets in the refrigerant output from the evaporation portion, reducing the amount of liquid refrigerant therein, making the refrigerant entering the compressor safer and more reliable, and improving the stability and reliability of the compressor.

[0031] Further features and advantages of the present invention will become apparent from the following detailed description of exemplary embodiments of the present invention with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] The drawings described herein are used to provide a further understanding of the present invention and constitute a part of this application. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0033] Figure 1 This is a schematic structural diagram of a heat pipe condenser desuperheating system according to an embodiment of the present invention;

[0034] Figure 2 for Figure 1 A schematic structural diagram of a partial cross-section of a heat pipe condenser desuperheating system from another angle is shown;

[0035] Figure 3 for Figure 1 A schematic structural diagram of a partial cross-section of a heat pipe condenser desuperheating system shown;

[0036] Figure 4 for Figure 1 A schematic structural diagram of a partial cross-section of a heat pipe condenser desuperheating system from another angle is shown;

[0037] Figure 5 for Figure 1 The schematic diagram of the structure of the heat pipe assembly of the heat pipe condenser desuperheating system shown;

[0038] Figure 6 for Figure 5 A schematic structural diagram of the heat pipe assembly from another angle is shown;

[0039] Figure 7 for Figure 5 A schematic structural diagram of the evaporation section of the heat pipe assembly shown;

[0040] Figure 8 for Figure 7 A schematic structural diagram of the evaporation section of the heat pipe assembly from another angle is shown;

[0041] Figure 9 for Figure 7 A schematic structural diagram of the evaporation section of the heat pipe assembly shown at another angle;

[0042] Figure 10 This is a schematic structural diagram of the evaporation section wick of a heat pipe assembly according to another embodiment of the present invention;

[0043] Figure 11 for Figure 10 The AA cross-sectional structure diagram of the evaporation section of the heat pipe assembly shown in FIG.

[0044] Figure 12 This is a schematic structural diagram of fins surrounding the evaporation section of a heat pipe assembly according to another embodiment of the present invention;

[0045] Figure 13 for Figure 12 A schematic structural diagram of the fin at another angle shown;

[0046] Figure 14 This is a schematic structural diagram of fins surrounding the evaporation section tube core of a heat pipe assembly according to another embodiment of the present invention;

[0047] Figure 15 for Figure 14 A schematic structural diagram of the fin at another angle shown;

[0048] Figure 16 This is a schematic structural diagram of fins surrounding the evaporation section tube core of a heat pipe assembly according to another embodiment of the present invention;

[0049] Figure 17 for Figure 16 A schematic structural diagram of the fin at another angle shown;

[0050] Figure 18 for Figure 7 A schematic structural diagram of the first support plate of the heat pipe assembly shown;

[0051] Figure 19 for Figure 18 A schematic structural diagram of the first support plate at another angle is shown;

[0052] Figure 20 for Figure 5 A schematic structural diagram of the condensing section of the heat pipe assembly shown;

[0053] Figure 21 for Figure 20 A schematic structural diagram of the condensing section of the heat pipe assembly from another angle is shown;

[0054] Figure 22 for Figure 20 A schematic structural diagram of the condensing section of the heat pipe assembly shown at another angle;

[0055] Figure 23 This is a schematic structural diagram of a condensing section wick of a heat pipe assembly according to another embodiment of the present invention;

[0056] Figure 24 for Figure 23 The CC-direction cross-sectional structure diagram of the condensing section of the heat pipe assembly shown;

[0057] Figure 25 for Figure 23 The BB-cross-sectional structural diagram of the condensing section of the heat pipe assembly shown;

[0058] Figure 26 for Figure 23 The schematic diagram of the partial enlarged structure of the D portion of the condensing section of the heat pipe assembly shown;

[0059] Figure 27 for Figure 7 A schematic structural diagram of the second support plate of the heat pipe assembly shown;

[0060] Figure 28 for Figure 26 A schematic structural diagram of the second support plate from another angle is shown. DETAILED DESCRIPTION

[0061] The following will be combined with the accompanying 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, rather than all the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is in no way intended to limit the present invention and its application or use. 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.

[0062] Unless otherwise specifically stated, the relative arrangement of the parts and steps, the numerical expressions and the numerical values ​​set forth in these embodiments do not limit the scope of the present invention. At the same time, it should be understood that, for ease of description, the sizes of the various parts shown in the drawings are not drawn according to the actual proportional relationship. The techniques, methods and equipment known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, the techniques, methods and equipment should be considered as part of the authorization specification. In all examples shown and discussed here, any specific values ​​should be interpreted as being merely exemplary and not as limiting. Therefore, other examples of the exemplary embodiments may have different values. It should be noted that similar numbers and letters represent similar items in the following figures, and therefore, once an item is defined in one figure, it does not need to be further discussed in subsequent figures.

[0063] In the description of the present invention, it should be understood that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of the present invention.

[0064] In the description of the present invention, it should be noted that, unless otherwise specified or limited, the terms "mounted," "connected," and "connected" should be understood broadly. For example, they may refer to fixed connections, detachable connections, or integral connections; they may refer to direct connections or indirect connections through an intermediary. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on the specific circumstances.

[0065] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used herein to describe the spatial positional relationship of a device or feature to other devices or features as shown in the figures. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figures. For example, if the device in the drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0066] like Figures 1 to 4 As shown, the heat pipe condenser desuperheating system of this embodiment includes a condenser 1 , a compressor, an evaporator 2 and a heat pipe assembly 3 .

[0067] The condenser 1 includes a condensing portion 11 for condensing the refrigerant. The refrigeration system includes four major components: an evaporator, a compressor, a condenser, and an expansion device. The condenser 1, the compressor, and the evaporator of this embodiment are the four major components of the refrigeration system. The evaporator 2 includes an evaporating portion 21 connected to the compressor. The evaporator 2 evaporates the refrigerant (also known as refrigerant, refrigerant) through the evaporating portion 21 and outputs it to the compressor for compression. The compressor is connected to the condensing portion 11, and the compressor is used to compress the refrigerant transported from the evaporator and output it to the condensing portion 11 for condensation.

[0068] A heat pipe is a heat transfer element, also known as a thermal superconductor, consisting of an evaporation section, an insulation section, and a condensation section. The cold and hot fluids conduct heat transfer through a coupled evaporation-condensation phase change process with the working medium in the heat pipe. The cold and hot fluids then pass through the heat pipe, a "heat transfer bridge," to achieve heat transfer without actual contact between the two. The specific working process is as follows: the medium in the evaporation section of the heat pipe absorbs the heat from the hot fluid outside the tube and evaporates into a gaseous state (at the same time, the hot fluid outside the tube releases heat and its temperature drops or condenses). The gaseous refrigerant flows to the condensation section of the heat pipe and transfers heat to the cold fluid outside the condensation section. The medium in the tube is condensed into a liquid state (at the same time, the cold fluid outside the tube absorbs heat and its temperature rises or evaporates). The liquid working fluid flows back to the evaporation section of the heat pipe under the action of gravity or capillary force and continues to participate in the cyclic heat transfer. The entire process achieves rapid heat transfer between the two fluids outside the tube through the evaporation-condensation cycle of the medium in the heat pipe.

[0069] The heat pipe assembly 3 of this embodiment uses the above-mentioned heat pipe to transfer heat. Figures 1 to 6As shown, the heat pipe assembly 3 includes an evaporator section 31 and a condenser section 32 connected to the evaporator section 31. A cooling medium circulates between the evaporator section 31 and the condenser section 32. The evaporator section 31 is located between the condenser section 11 and the compressor to exchange heat between the compressed refrigerant output by the compressor and the cooling medium in the evaporator section 31 before entering the condenser section 11. That is, the refrigerant output by the compressor is first cooled by the cooling medium in the evaporator section 31 before being condensed in the condenser section 11. The high-temperature, high-pressure superheated refrigerant output by the compressor is at least partially or completely cooled to saturated steam before entering the condenser section 11 of the condenser 1 for condensation. Since the refrigerant entering the condenser section 11 undergoes phase change heat transfer with the condenser section 11, releasing latent heat, the heat exchange efficiency between the condenser section 11 and the refrigerant is greatly improved. The condenser section 32 is located between the evaporator section 21 and the compressor to exchange heat between the evaporated refrigerant output by the evaporator section 21 and the cooling medium in the condenser section 32 before entering the compressor. After the evaporation section 31 of the heat pipe assembly 3 exchanges heat with the refrigerant before entering the condenser section 11, the cooling medium in the evaporation section 31 absorbs the refrigerant's heat and is transferred to the condenser section 32. The refrigerant output from the evaporator section of the evaporator 2 evaporates the refrigerant and exchanges heat with the cooling medium in the condenser section 32 before entering the compressor for compression. The cooling medium transfers the heat transferred from the evaporation section to the refrigerant. The refrigerant output from the evaporation section contains a small amount of liquid refrigerant. After the condenser section 32 heats the refrigerant output from the evaporation section, it reduces the liquid refrigerant content and converts it into gaseous refrigerant, which is then output to the compressor, reducing the risk of liquid inhalation by the compressor. After releasing heat, the cooling medium in the condenser section 32 circulates back to the evaporation section 31 of the heat pipe assembly to absorb heat again.

[0070] The droplets (liquid refrigerant) in the refrigerant output by the evaporator are a hazardous factor that affects the safe operation of the compressor and must be removed before entering the compressor. In known technologies, a filter (also called a demister) is often used to filter them out (traditional method), or electric heating or other methods are used to heat them to evaporate / vaporize them. The heat pipe condenser desuperheating system of this embodiment is configured by arranging the evaporation section 31 of the heat pipe assembly 3 between the condensing part 11 of the condenser 1 and the compressor and the condensation section 32 of the heat pipe assembly 3 between the evaporating part 21 of the evaporator 2 and the compressor. The heat pipe assembly 3 is used to cool the refrigerant before it enters the condensing part 11 and convert it into a saturated vapor state. The heat exchange efficiency of the refrigerant after the conversion can be greatly improved in the condenser 1, and the structure of the condenser 1 can be simplified. At the same time, the heat pipe assembly 3 can efficiently transfer the heat absorbed by the evaporation section 31 to the evaporator 2, and use the heat to heat the refrigerant output from the evaporation part 21 of the evaporator 2, so that the droplets in the refrigerant output from the evaporation part 21 can be evaporated, reducing the liquid refrigerant therein, making the refrigerant entering the compressor safer and more reliable, thereby improving the stability and reliability of the compressor.

[0071] In some embodiments, as Figures 20 to 26As shown, the condensing section 32 includes one or more condensing section tube cores 321 for heat exchange between the evaporated refrigerant output from the evaporator 21 and the cooling medium. The outer surface of the condensing section tube core 321 is provided with a porous structure 3212 for heat exchange with the refrigerant. In the embodiment shown in the figure, the porous structure 3212 includes multiple recessed holes arranged circumferentially around the condensing section tube core 321. The multiple recessed holes are evenly spaced. In the embodiment shown in the figure, the recessed holes are blind holes. Evaporation is a latent heat transfer method, which has a heat transfer intensity more than 10 times that of sensible heat. This type of heat transfer requires a certain number of vaporization cores. The porous structure is a large number of sealed evaporation cavities containing a large number of vaporization cores, which enables the working medium to boil or / and evaporate at a low wall superheat. The porous structure 3212 on the outer surface of the condensing section tube core of the heat pipe assembly is used to efficiently evaporate liquid droplets entrained in the gaseous refrigerant, utilizing the latent heat of droplet evaporation (from liquid to gas) rather than the sensible heat of temperature increase alone. The evaporated refrigerant output from the evaporation section 21 exchanges heat with the cooling medium in the condensation section 32 on the surface of the condensation section tube core 321, so that the liquid refrigerant in the refrigerant evaporates after being heated. The surface of the condensation section tube core 321 is provided with a porous structure, which can greatly improve the evaporation effect of the liquid refrigerant in the refrigerant, while not significantly increasing the superheat temperature of the gaseous refrigerant entering the compressor. The porous structure provided in this embodiment can ensure the evaporation effect, thereby eliminating the gas-liquid filter or demister assembly in the evaporator structure design of the prior art (removing the liquid entrained in the evaporated gaseous refrigerant through gravity sedimentation, inertial collision and filtering action of the filter), and at the same time, the pipe layout height of the evaporator can be appropriately increased (in the existing design of the evaporator using a gas-liquid filter, in order to ensure a certain droplet sedimentation height, the pipe layout height of the tube bundle of the evaporation section of the evaporator generally does not exceed the center line), thereby making the evaporator tube bundle design more compact.

[0072] In some embodiments, as Figure 5 As shown, the evaporation section 31 includes an evaporation section wick 311, and the condensation section 32 includes a condensation section wick 321. The length of the condensation section wick 321 is shorter than that of the evaporation section wick 311. Because the surface of the condensation section wick 321 is provided with a porous structure, the evaporation effect of the refrigerant is greatly improved, so that the heat exchange efficiency of the condensation section of the heat pipe assembly can be lower than that of the evaporation section 31. Setting the length of the condensation section wick 321 to be shorter than that of the evaporation section wick 311 can ensure the evaporation effect of the liquid refrigerant while preventing the temperature of the evaporated gaseous refrigerant from being too high. At the same time, it can also make the structure of the condensation section of the heat pipe assembly more compact.

[0073] In some embodiments, the materials of the evaporation section tube core and the condensation section tube core may include copper, copper alloy, nickel, nickel alloy, aluminum, aluminum alloy, carbon steel, low alloy steel, stainless steel, etc.

[0074] In some embodiments, as Figures 7 to 9 ,like Figures 20 to 25 As shown, the evaporator section 31 includes one or more evaporator section tube cores 311 for heat exchange between the compressed refrigerant output by the compressor and the cooling medium. The condenser section 32 includes one or more condenser section tube cores 321 for heat exchange between the evaporated refrigerant output by the evaporator 21 and the cooling medium. The inner tube walls of the evaporator section tube cores 311 and / or the condenser section tube cores 321 are provided with a plurality of circumferentially distributed strip grooves 34. These strip grooves 34 extend axially along the inner tube walls to provide capillary force during the return flow of the cooling medium from the condenser section 32 to the evaporator section 31. In the embodiment shown in the figure, the inner walls of both the evaporator section tube cores 311 and condenser section tube cores 321 are provided with strip grooves 34, which are parallel to each other. The provision of these strip grooves 34 provides capillary force, facilitating the return flow of the cooling medium from the condenser section to the evaporator section. The strip grooves 34 are integrally formed with the inner tube walls of the tube cores, reducing thermal resistance and enhancing heat transfer efficiency from the evaporator section to the condenser section.

[0075] In some embodiments, as Figures 7 to 17 As shown, to enhance the cooling effect of the evaporator section 31 on the refrigerant, the evaporator section 31 includes one or more evaporator section tube cores 311 for heat exchange between the compressed refrigerant output by the compressor and the cooling medium. The outer surface of the evaporator section tube core 311 is smooth. The evaporator section 311 also includes fins 312 disposed around the outer surface of the evaporator section tube core 311. The fins 312 are provided with tube holes 3121 for mounting the evaporator section tube core 311. The outer surface of the evaporator section tube core 311 is smooth. The evaporator section tube core 311 is expanded and connected to the fins, ensuring a closer fit with the fins 312 and improving heat exchange. The fin material can be a metal material with good thermal conductivity and ductility, such as copper or aluminum. The fins 312 can be flat, corrugated, or windowed. Flat fins are relatively thin, flat metal sheets without any additional structures, resulting in a simple structure and low cost. Corrugated wings are fins with regular crests and troughs (folded up and down or left and right, similar to the structure of a paper folding fan). The heat exchange surface is an angled slope, which allows the gas to be regularly disturbed on its surface. Compared with flat wings, the heat exchange area is increased. Corrugated wings have better heat exchange effects than flat wings, but the cost is higher. Windowed wings are made by cutting some rectangular or trapezoidal small openings (narrow gaps) in different directions on the basis of flat wings, and then tilting the material at the small openings (for example, stamping them out). Windowed wings combine the principle of field synergy and enhance heat transfer by changing the synergy of the external flow field and the heat transfer field (making the angle between the fluid flow direction and the heat transfer direction smaller). This type of fin is expensive, but the heat exchange efficiency is higher than that of flat wings and corrugated wings. In this embodiment, flat wings, corrugated wings or windowed wings can be set for the evaporation section tube core 311 based on the comprehensive consideration of heat exchange effect and cost.

[0076] In some embodiments, as Figures 1 to 7 , Figures 20 to 22 As shown, the evaporation section 31 includes a plurality of evaporation section tube cores 311 for heat exchange between the compressed refrigerant output by the compressor and the cooling medium. The condensation section 32 includes a plurality of condensation section tube cores 321 for heat exchange between the evaporated refrigerant output by the evaporator 21 and the cooling medium. The heat pipe assembly 3 also includes an insulating tube 331 whose ends respectively connect the plurality of evaporation section tube cores 311 and the plurality of condensation section tube cores 321. In this embodiment, the evaporation section 31 and the condensation section 32 of the heat pipe assembly 3 are connected by the insulating section 33. Since the heat exchange of the heat pipe assembly mainly occurs in the evaporation section and the condensation section, the insulating section only serves as a connection and does not exchange heat with the refrigerant. Therefore, the number of insulating tubes in the insulating section can be minimized. In this embodiment, the ends of a single insulating tube are respectively connected to the plurality of evaporation section tube cores 311 and the plurality of condensation section tube cores 321. This ensures the flow of cooling medium in the evaporation section and the condensation section while saving material. The small number of insulating tubes 331 also facilitates the flexible spatial arrangement of the heat pipe assembly.

[0077] In some embodiments, as Figure 2 、 Figure 6 、 Figure 9 and Figure 22 As shown, a heat pipe layer is formed by an insulated pipe and multiple evaporation section pipe cores 311 and multiple condensation section pipe cores 321 connected at both ends. The heat pipe assembly 3 includes multiple stacked heat pipe layers. The stacking of multiple heat pipe layers creates a compact structure and facilitates adjustment by increasing or decreasing the number of heat pipe layers based on heat exchange requirements.

[0078] In some embodiments, as Figures 1 to 4 As shown, the condenser 1 includes a first barrel 12, with the condensing portion 11 and the evaporating section 31 both disposed within the first barrel 12. The first barrel 12 is provided with an air inlet 13 connected to the compressor for receiving the refrigerant output by the compressor, and the evaporating section 31 is located between the air inlet 13 and the condensing portion 11. Providing the evaporating section 31 within the first barrel of the condenser 1 makes the structure of the heat pipe condenser desuperheating system more compact, and also helps to improve the cooling effect of the heat pipe assembly on the refrigerant before it enters the condensing portion 11.

[0079] In some embodiments, as Figures 7 to 9 , Figure 18 and Figure 19As shown, the first barrel 12 also includes a first support plate 313 disposed between the evaporation section 31 and the condensation section 11 to support the evaporation section 31. The first support plate 313 is provided with a first elongated hole 3131 extending along the axial direction of the first barrel 12 and ribs 3132 connecting the two ends of the first elongated hole 3131 along the length direction. The provision of the first support plate 313 can provide stable support for the evaporation section 31 of the heat pipe assembly. The provision of the first elongated hole 3131 and the ribs 3132 can not only prevent the refrigerant cooled by the evaporation section 31 from entering the condensation section 11, but also strengthen the strength of the first elongated hole 3131. In some embodiments, the first support plate 313 is connected to the first barrel at all four ends along the length and width directions.

[0080] In some embodiments, the first cylinder 12 is further provided with a cooling water inlet 41 and a cooling water outlet 42 that communicate with the condensation section 11. The cooling water inlet 41 and the cooling water outlet 42 are respectively used to introduce cooling water for condensing the refrigerant into the condensation section 11 and to output the cooling water after the refrigerant is condensed in the condensation section 11. This embodiment condenses the refrigerant using cooling water and is suitable for use in water-cooled air conditioning units. In some embodiments, the condenser and evaporator are shell-and-tube condensers and shell-and-tube evaporators, respectively.

[0081] In some embodiments, the evaporator 2 includes a second cylinder 22, and the evaporation portion 21 and the condensation section 32 are both arranged in the second cylinder 22. The second cylinder 22 is provided with an outlet 23 for outputting the evaporated refrigerant to the compressor, which is connected to the compressor. The condensation section 32 is located between the outlet 23 and the evaporation portion 21. The condensation section 32 is arranged in the first cylinder of the evaporator 2, making the structure of the heat pipe condenser desuperheating system more compact, and also helping to improve the evaporation effect of the heat pipe assembly on the refrigerant output from the evaporation portion 21 of the evaporator 2. Figure 23-25 As shown, a porous structure is provided on the outer surface of the portion of the condensing section tube core 321 corresponding to the evaporating portion and located in the first cylinder 22. This portion exchanges heat with the refrigerant output from the evaporating portion, and the outer surface of the end of the condensing section tube core 321 close to the insulating tube 331 is a smooth surface.

[0082] In some embodiments, the second barrel 22 further includes a second support plate 323 disposed between the condensing section 32 and the evaporating portion 21 to support the condensing section 32. The second support plate 323 is provided with a second elongated hole 3231 extending axially along the second barrel 22 and transverse support plates 322 connecting the two ends of the elongated hole along the width direction. The second support plate 323 provides stable support for the condensing section 32 of the heat pipe assembly. The second elongated hole 3231 and transverse support plates 322 ensure that the refrigerant cooled by the condensing section 32 enters the condensing portion 11 without affecting the strength of the second elongated hole 3231. In some embodiments, the multiple evaporating section tube cores 321 of the evaporating section 32 pass through the transverse support plate 322 and are supported and positioned by the transverse support plate 321.

[0083] In some embodiments, the second cylinder 22 is also provided with a chilled water inlet 51 and a chilled water outlet 52 connected to the evaporation part 21. The chilled water inlet 51 and the chilled water outlet 52 are respectively used to input liquid water for evaporating refrigerant into the evaporation part 21 and output liquid water after the refrigerant evaporates in the evaporation part 21. The liquid water can be used under indoor temperature conditions.

[0084] In some embodiments, a refrigeration system is also disclosed, comprising any of the above-mentioned heat pipe condenser desuperheating systems.

[0085] In some embodiments, the refrigeration system is an air conditioner.

[0086] In some embodiments, a method for desuperheating a heat pipe condenser desuperheating system is also disclosed, comprising:

[0087] Before the compressed refrigerant output by the compressor enters the condensation section 11, the cooling medium exchanges heat with the refrigerant in the evaporation section 31, so that the refrigerant is cooled to a saturated vapor state before entering the condensation section 11;

[0088] After the cooling medium completes the heat exchange with the refrigerant in the evaporation section 31, it enters the condensation section 32 to exchange heat with the evaporated refrigerant output from the evaporation part 21, so that the evaporated refrigerant output from the evaporation part 21 evaporates the liquid refrigerant into gaseous state when entering the compressor;

[0089] The cooling medium returns to the evaporation section 31 after completing the heat exchange with the refrigerant in the condensation section 32 .

[0090] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit the present invention. Although the present invention has been described in detail with reference to preferred embodiments, ordinary technicians in the field should understand that the specific implementation methods of the present invention can still be modified or some technical features can be replaced by equivalents without departing from the spirit of the technical solutions of the present invention. They should all be included in the scope of the technical solutions claimed for protection by the present invention.

Claims

1. A heat pipe condenser desuperheating system, characterized in that: include: A condenser (1) comprising a condensing portion (11) for condensing a refrigerant; A compressor connected to the condensation section (11) for compressing the refrigerant and outputting the refrigerant to the condensation section (11) for condensation; An evaporator (2) includes an evaporation portion (21) connected to the compressor and configured to evaporate the refrigerant and output it to the compressor for compression; A heat pipe assembly (3) comprises an evaporation section (31), a condensation section (32) connected to the evaporation section (31), and a cooling medium circulating between the evaporation section (31) and the condensation section (32), wherein the evaporation section (31) is arranged between the condensation section (11) and the compressor so that the compressed refrigerant output by the compressor is heat-exchanged with the cooling medium in the evaporation section (31) before entering the condensation section (11), and the condensation section (32) is arranged between the evaporation section (21) and the compressor so that the evaporated refrigerant output by the evaporation section (21) is heat-exchanged with the cooling medium in the condensation section (32) before entering the compressor. The condensing section (32) includes one or more condensing section tube cores (321) for performing heat exchange between the evaporated refrigerant output from the evaporating portion (21) and the cooling medium. The outer surface of the condensing section tube core (321) is provided with a porous structure (3212) for performing heat exchange with the refrigerant. The porous structure (3212) includes a plurality of concave holes arranged circumferentially around the condensing section tube core (321). The plurality of concave holes are evenly arranged. The evaporating section (31) includes an evaporating section tube core (311). The condensing section (32) includes a condensing section tube core (321). The length of the condensing section tube core (321) is less than the length of the evaporating section tube core (311).

2. The heat pipe condenser desuperheating system according to claim 1, characterized in that: The evaporation section (31) includes one or more evaporation section tube cores (311) for performing heat exchange between the compressed refrigerant output by the compressor and the cooling medium, and the condensation section (32) includes one or more condensation section tube cores (321) for performing heat exchange between the evaporated refrigerant output by the evaporation section (21) and the cooling medium, and the inner tube wall of the evaporation section tube core (311) and / or the condensation section tube core (321) is provided with a plurality of strip grooves (34) distributed along the circumferential direction, and the strip grooves (34) extend along the axial direction of the inner tube wall to provide capillary force when the cooling medium flows back from the condensation section (32) to the evaporation section (31).

3. The heat pipe condenser desuperheating system according to claim 1, characterized in that: The evaporation section (31) includes one or more evaporation section tube cores (311) for performing heat exchange between the compressed refrigerant output by the compressor and the cooling medium. The outer surface of the evaporation section tube core (311) is a smooth surface. The evaporation section (31) also includes fins (312) arranged around the outer surface of the evaporation section tube core (311). The fins (312) are flat fins, corrugated fins, or window fins.

4. The heat pipe condenser desuperheating system according to claim 1, characterized in that: The evaporation section (31) includes a plurality of evaporation section tube cores (311) for performing heat exchange between the compressed refrigerant output by the compressor and the cooling medium; the condensation section (32) includes a plurality of condensation section tube cores (321) for performing heat exchange between the evaporated refrigerant output by the evaporation portion (21) and the cooling medium; and the heat pipe assembly (3) further includes an insulating tube (331) having two ends respectively connected to the plurality of evaporation section tube cores (311) and the plurality of condensation section tube cores (321).

5. The heat pipe condenser desuperheating system according to claim 4, characterized in that: The insulating tube (331) and the multiple evaporation section tube cores (311) and the multiple condensation section tube cores (321) connected at both ends thereof form a heat pipe layer, and the heat pipe assembly (3) includes multiple stacked heat pipe layers.

6. The heat pipe condenser desuperheating system according to any one of claims 1 to 5, characterized in that: The condenser (1) includes a first cylinder (12), the condensing portion (11) and the evaporating section (31) are both arranged in the first cylinder (12), the first cylinder (12) is provided with an air inlet (13) connected to the compressor for receiving the refrigerant output by the compressor, and the evaporating section (31) is located between the air inlet (13) and the condensing portion (11).

7. The heat pipe condenser desuperheating system according to claim 6, characterized in that: The first cylinder (12) further includes a first support plate (313) disposed between the evaporation section (31) and the condensation section (11) for supporting the evaporation section (31), wherein the first support plate (313) is provided with a first elongated hole (3131) extending along the axial direction of the first cylinder (12) and ribs connecting the two ends of the first elongated hole (3131) along the length direction.

8. The heat pipe condenser desuperheating system according to claim 6, characterized in that: The first cylinder (12) is also provided with a cooling water inlet (41) and a cooling water outlet (42) which are connected to the condensation section (11). The cooling water inlet (41) and the cooling water outlet (42) are respectively used to introduce cooling water for condensing the refrigerant into the condensation section (11) and to output cooling water after condensing the refrigerant in the condensation section (11).

9. The heat pipe condenser desuperheating system according to any one of claims 1 to 5, characterized in that: The evaporator (2) includes a second cylinder (22), the evaporation portion (21) and the condensation section (32) are both arranged in the second cylinder (22), the second cylinder (22) is provided with an outlet (23) connected to the compressor for outputting evaporated refrigerant to the compressor, and the condensation section (32) is located between the outlet (23) and the evaporation portion (21).

10. The heat pipe condenser desuperheating system according to claim 9, characterized in that: The second cylinder (22) further includes a second support plate (323) provided between the condensing section (32) and the evaporating portion (21) for supporting the condensing section (32), wherein the second support plate (323) is provided with a second elongated hole (3231) extending along the axial direction of the second cylinder (22) and a transverse support plate (322) connecting both ends of the second elongated hole (3231) in the width direction.

11. The heat pipe condenser desuperheating system according to claim 9, characterized in that: The second cylinder (22) is further provided with a chilled water inlet (51) and a chilled water outlet (52) which are in communication with the evaporation portion (21). The chilled water inlet (51) and the chilled water outlet (52) are respectively used to input liquid water for evaporating the refrigerant into the evaporation portion (21) and to output liquid water after the refrigerant is evaporated in the evaporation portion (21).

12. A refrigeration system, characterized in that: The invention comprises a heat pipe condenser desuperheating system according to any one of claims 1 to 11.

13. An air conditioner, characterized in that: Comprising the refrigeration system of claim 12.

14. A desuperheating method using the heat pipe condenser desuperheating system according to any one of claims 1 to 11, characterized in that: include: Before the compressed refrigerant output by the compressor enters the condensation section (11), the cooling medium is heat-exchanged with the refrigerant in the evaporation section (31), so that the refrigerant is cooled to a saturated vapor state before entering the condensation section (11); After the cooling medium completes heat exchange with the refrigerant in the evaporation section (31), it enters the condensation section (32) and performs heat exchange with the evaporated refrigerant output from the evaporation section (21), so that the evaporated refrigerant output from the evaporation section (21) evaporates the liquid refrigerant into gaseous state before entering the compressor; The cooling medium returns to the evaporation section (31) after completing heat exchange with the refrigerant in the condensation section (32).

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