Heat exchanger, heat pump system and drying equipment

Abstract

The invention provides a heat exchanger, a heat pump system and drying equipment, the heat exchanger is used for the drying equipment, the heat exchanger is provided with a windward side and a leeward side, the direction from the windward side to the leeward side is the first direction, the drying equipment is provided with a drying chamber and a heat exchanger arranged with the drying chamber in the second direction, and a heat exchange cavity where the heat exchanger is located communicates with the drying chamber. The first size of the heat exchanger in the second direction is smaller than the second size in the first direction; wherein the first direction is perpendicular to the second direction. The heat exchange efficiency of the heat pump system can be improved, and the structural compactness of the drying equipment is improved.

Description

Technical Field

[0001] This application relates to the field of household appliance technology, and in particular to a heat exchanger, heat pump system and drying equipment. Background Technology

[0002] In today's society, heat pump systems are widely used in various household appliances that require heat exchange functions. For example, heat pump systems are used in drying equipment to achieve a drying effect. In existing technologies, common heat pump systems have low heat exchange efficiency, and the drying equipment has a large structural size, requiring structural optimization. Summary of the Invention

[0003] This application provides a heat exchanger, a heat pump system, and a drying equipment, which can improve the heat exchange efficiency of the heat pump system and improve the structural compactness of the drying equipment.

[0004] To solve the above-mentioned technical problems, this application provides a heat exchanger for a drying device. The heat exchanger has a windward side and a leeward side. The direction from the windward side to the leeward side is a first direction. The drying device has a drying chamber and heat exchangers arranged along a second direction with the drying chamber. The heat exchange chamber where the heat exchanger is located is connected to the drying chamber. The first dimension of the heat exchanger along the second direction is smaller than the second dimension along the first direction. The first direction is perpendicular to the second direction.

[0005] To solve the above-mentioned technical problems, this application further provides a heat pump system, which includes a compressor, an evaporator, and a condenser. The evaporator includes the aforementioned heat exchanger. The compressor, condenser, and evaporator form a refrigerant circulation channel. The evaporator and condenser are used to be installed in the heat exchange chamber.

[0006] To solve the above-mentioned technical problems, this application further provides a drying device, which includes a drying chamber, an air duct shell, and the aforementioned heat pump system. The air duct shell forms a heat exchange chamber that communicates with the drying chamber. At least an evaporator and a condenser are disposed in the heat exchange chamber. The evaporator and the condenser are arranged in a horizontal direction, and the second direction is the direction of gravity.

[0007] The beneficial effects of this application are as follows: The heat exchanger in this application is located in a heat exchange chamber that is connected to the drying chamber, facilitating airflow between the heat exchange chamber and the drying chamber, enabling heat exchange between the heat exchanger and the drying chamber, and improving the drying efficiency of the drying chamber; the heat exchanger being located inside the heat exchange chamber reduces interference from the external environment, improving its working efficiency and reducing the probability of damage; the arrangement of the heat exchanger and the drying chamber along the second direction optimizes their layout, simplifies structural design, and improves the reliability of their operation. For example, when the second direction is the direction of gravity and the heat exchanger is located above the drying chamber, this arrangement allows the drying chamber to provide some support for the heat exchanger, improving the positional stability of the heat exchanger; since the heat exchanger and the drying chamber are arranged along the second direction, the first dimension of the heat exchanger along the second direction is smaller than its second dimension along the first direction, which facilitates reducing the overall size of the drying equipment in the second direction and improving the structural compactness of the drying equipment; and it also facilitates increasing the total heat exchange area of ​​the heat exchanger by increasing the second dimension, thereby improving the heat exchange efficiency of the heat pump system. Attached Figure Description

[0008] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort. Wherein:

[0009] Figure 1 This is a schematic diagram of the structure of an embodiment of the drying equipment of this application;

[0010] Figure 2 yes Figure 1 A cross-sectional structural diagram of the embodiment;

[0011] Figure 3 This is a partial structural schematic diagram of the heat pump system of the first embodiment of this application;

[0012] Figure 4 yes Figure 3 Side view of the embodiment;

[0013] Figure 5 This is a schematic diagram of the structure of an embodiment of the heat exchanger of this application;

[0014] Figure 6 This is a schematic diagram of the structure of an embodiment of the heat exchanger of this application;

[0015] Figure 7 This is a schematic diagram of the structure of an embodiment of the heat exchanger of this application;

[0016] Figure 8 This is a partial structural schematic diagram of the second embodiment of the heat pump system of this application;

[0017] Figure 9 yes Figure 8 Side view of the embodiment;

[0018] Figure 10 This is a schematic diagram of the structure of an embodiment of the heat exchanger of this application. Detailed Implementation

[0019] In the following description, specific details such as particular system architectures and techniques are set forth for illustrative purposes and not for limitation, in order to provide a thorough understanding of the embodiments of this application. However, those skilled in the art will understand that this application may also be implemented in other embodiments without these specific details. In other instances, detailed descriptions of well-known systems, apparatuses, circuits, and methods have been omitted so as not to obscure the description of this application with unnecessary detail.

[0020] The terms “first,” “second,” etc., used in this application are used to distinguish different objects, not to describe a specific order. Furthermore, the terms “comprising” and “having,” and any variations thereof, are intended to cover non-exclusive inclusion. It should be understood that, when used in this specification and the appended claims, the term “comprising” indicates the presence of the described feature, integral, step, operation, element, and / or component, but does not exclude the presence or addition of one or more other features, integrals, steps, operations, elements, components, and / or collections thereof. It should also be understood that the terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the application. As used in this specification and the appended claims, the singular forms “a,” “an,” and “the” are intended to include the plural forms unless the context clearly indicates otherwise. It should also be further understood that the term “and / or,” as used in this specification and the appended claims, refers to any combination and all possible combinations of one or more of the associated listed items, and includes such combinations.

[0021] It should be noted that when one element is fixed to another element, this includes fixing the element directly to the other element or fixing the element to the other element through at least one other intermediate element. When one element is connected to another element, this includes connecting the element directly to the other element or connecting the element to the other element through at least one other intermediate element.

[0022] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.

[0023] This application first proposes a heat exchanger, such as Figures 1 to 10 As shown. See also Figures 1 to 5 The heat exchanger 100 is used in the drying equipment 10. The heat exchanger 100 has a windward side and a leeward side. The direction from the windward side to the leeward side is the first direction x. The drying equipment 10 has a drying chamber 200 and heat exchangers 100 arranged in the drying chamber 200 along the second direction y. The heat exchange chamber where the heat exchanger 100 is located is connected to the drying chamber 200. The first dimension Hf of the heat exchanger 100 along the second direction y is smaller than the second dimension Tf along the first direction x. The first direction x is perpendicular to the second direction y.

[0024] It should be noted that the drying equipment 10 in this application can be, for example, a clothes dryer, a washer-dryer combo, a dryer, or other equipment with at least a drying function; the drying chamber 200 is used to hold the items to be dried. The drying chamber 200 in this application can be a separate drying chamber 200 or a washer-dryer, and is not specifically limited; the heat exchanger 100 and the drying chamber 200 are arranged along the second direction y, which means that the projection of the heat exchanger 100 along the direction perpendicular to the second direction y is completely offset from and does not overlap with the projection of the drying chamber 200 along that direction; in this application, projection refers to orthographic projection; the first direction x refers to the flow direction of the airflow through the heat exchanger 100.

[0025] The heat exchanger 100 is located in a heat exchange chamber that is connected to the drying chamber 200, facilitating airflow within both chambers and improving heat exchange efficiency. The placement of the heat exchanger 100 within the heat exchange chamber reduces external environmental interference, improving its efficiency and reducing the likelihood of damage. The arrangement of the heat exchanger 100 and the drying chamber 200 along the second direction y optimizes their layout, simplifies structural design, and enhances operational reliability. For example, when the second direction y is the direction of gravity and the heat exchanger 100 is positioned... When positioned above the drying chamber 200, this arrangement facilitates the drying chamber 200 in providing support for the heat exchanger 100, thereby improving the positional stability of the heat exchanger 100. Since the heat exchanger 100 and the drying chamber 200 are arranged along the second direction y, setting the first dimension Hf of the heat exchanger 100 along the second direction y to be smaller than its second dimension Tf along the first direction x facilitates reducing the overall size of the drying equipment 10 in the second direction y, thereby improving the structural compactness of the drying equipment 10. Furthermore, it facilitates increasing the total heat exchange area of ​​the heat exchanger 100 by increasing the second dimension Tf, thereby improving the heat exchange efficiency of the heat pump system 11.

[0026] Furthermore, the first direction x is set perpendicular to the second direction y, which facilitates the airflow into the heat exchanger 100 and reduces the interference of the drying chamber 200 on the airflow.

[0027] In some embodiments, see Figure 5 The heat exchanger 100 includes fins 110 and refrigerant pipes 120. The fins 110 extend along the second direction y and the first direction x. The refrigerant pipes 120 are disposed on the fins 110. The first dimension Hf of the fins 110 along the second direction y is smaller than the second dimension Tf of the fins 110 along the first direction x.

[0028] It should be noted that the extension of fin 110 along the second direction y and the first direction x means that fin 110 extends in a plane perpendicular to its thickness direction to form its main heat exchange surface; the heat exchange medium for heat exchange flows inside the refrigerant pipe 120; the refrigerant pipe 120 is arranged on the fin 110 to facilitate the use of the fin 110 to increase the heat exchange efficiency between the refrigerant pipe 120 and the airflow.

[0029] The fins 110 extend along the second direction y and the first direction x, which helps to reduce the resistance encountered by the airflow when it flows through the heat exchanger 100, and facilitates heat exchange between the main heat exchange surface of the fins 110 and the airflow. The first dimension Hf of the fins 110 along the second direction y is smaller than the second dimension Tf of the fins 110 along the first direction x, which makes it easier to set the first dimension Hf of the heat exchanger 100 along the second direction y to be smaller than its second dimension Tf along the first direction x, thereby improving production convenience.

[0030] To further improve the heat exchange efficiency of the heat exchanger 100, in some embodiments, the ratio between the first dimension Hf and the second dimension Tf is set to 0.5 to 0.95.

[0031] Specifically, the ratio can be 0.5, 0.66, 0.68, 0.7, 0.72, 0.8, 0.85, 0.88, 0.9, 0.91, 0.93 or 0.95, etc., without any specific limitation.

[0032] This configuration allows the heat exchanger 100 to have a smaller size in the second direction y, and the heat exchange performance of the heat exchanger 100 can be guaranteed by increasing the second size Tf in the first direction x. Therefore, it is possible to achieve a higher heat exchange efficiency of the heat exchanger 100 with a smaller height space (i.e., the first size Hf), thereby improving the overall drying efficiency of the drying equipment 10.

[0033] For example, in one application scenario, the heat exchanger 100 of this embodiment is used as an evaporator, with an inlet air temperature of 45°C, an inlet air humidity of 70%, and an inlet air volume of 100 m³ / h. 3 / h to 140m 3When the ratio between the first dimension Hf and the second dimension Tf is 1.65, for example, with the first dimension Hf being 84 cm and the second dimension being 50.8 cm, the heat exchange efficiency of the evaporator per unit time is 1909 W. When the ratio between the first dimension Hf and the second dimension Tf is 0.63, for example, with the first dimension Hf being 58.5 cm and the second dimension being 92.8 cm, the heat exchange efficiency of the evaporator per unit time is 1909 W. The improved evaporator can increase the heat exchange efficiency by 11%.

[0034] In other embodiments, the ratio can be taken as other values ​​to achieve adaptive adjustment according to the actual product structure requirements, such as 0.45 or 0.96, etc., without being limited to any specific value.

[0035] In some embodiments, see Figure 6 The heat exchanger 100 includes a plurality of fins 110 spaced apart along a third direction z, with a spacing Fp between adjacent fins 110 of 1.4 mm to 2 mm; wherein the third direction z is perpendicular to the second direction y and the first direction x respectively.

[0036] It should be noted that the spacing Fp between adjacent fins 110 refers to the spacing Fp between adjacent fins 110 along the third direction z. This spacing Fp can be 1.4mm, 1.43mm, 1.45mm, 1.46mm, 1.5mm, 1.51mm, 1.55mm, 1.57mm, 1.6mm, 1.66mm, 1.7mm, 1.72mm, 1.78mm, 1.8mm, 1.85mm, 1.9mm, 1.92mm, 1.95mm, 1.98mm, or 2mm, etc., and there is no specific limitation.

[0037] The smaller the spacing distance Fp, the greater the heat exchange capacity per unit time, i.e., the higher the heat exchange efficiency. However, the air resistance of the heat exchanger 100 will also increase. Furthermore, if the spacing distance Fp is too small, for example less than 1.3 mm, foreign objects such as lint will more easily accumulate on the heat exchanger 100, affecting its heat exchange efficiency. Therefore, since the third direction z is perpendicular to the first direction x, the spacing distance Fp formed between adjacent fins 110 spaced along the third direction z can reduce the resistance encountered by the airflow through the heat exchanger 100, keeping the overall air resistance of the heat exchanger 100 at a low level. The spacing distance Fp is set within the range of 1.4 mm to 2 mm, which can reduce the overall size of the heat exchanger 100 while ensuring low air resistance, thus maintaining its heat exchange efficiency, improving its applicability, and reducing the risk of foreign objects such as lint accumulating on the heat exchanger 100. For example, when the second dimension Tf of the heat exchanger 100 along the first direction x is large (e.g., when the ratio between the first dimension Hf and the second dimension Tf is 0.5 to 0.95), setting the interval distance Fp to 1.4 mm to 2 mm can effectively reduce the wind resistance of the heat exchanger 100, enabling the heat exchanger 100 to achieve efficient heat exchange even when the second dimension Tf in the first direction x is large.

[0038] In other embodiments, the spacing between adjacent fins can be other values, such as 1.35 mm or 2.1 mm, depending on the different requirements for parameters such as heat exchange efficiency of the heat exchanger, and there is no specific limitation.

[0039] In some embodiments, the spacing distance Fp is 1.5 mm.

[0040] In one application scenario, the inlet air temperature of heat exchanger 100 is 45℃, the inlet air humidity is 70%, and the inlet air volume is 100m³. 3 / h to 140m 3 In the case of a heat exchanger with a flow rate of 1.5 mm / h, as the spacing distance Fp between adjacent fins 110 increases, the heat exchange capacity decreases. When the spacing distance Fp is greater than 1.6 mm, the decrease in heat exchange capacity increases significantly with the increase of Fp, meaning that the increase in spacing distance Fp has a greater impact on the decrease in heat exchange capacity. Conversely, as the spacing distance Fp between adjacent fins 110 increases, the air resistance of the heat exchanger also decreases. However, when the spacing distance Fp increases to greater than 1.6 mm, the decrease in air resistance becomes significantly smaller, meaning that the increase in spacing distance Fp contributes less and less to reducing air resistance. Therefore, to achieve lower air resistance and greater heat exchange capacity in the heat exchanger 100, a spacing distance Fp of 1.5 mm is preferred.

[0041] In some embodiments, the inlet air temperature can be set to 5°C to 50°C, the inlet air humidity can be set to 20% to 100%, and the air volume range can be set to 65m³ / h.3 / h to 220m 3 / h.

[0042] Setting the spacing Fp between adjacent fins 110 spaced along the third direction z to 1.5mm can effectively keep the air resistance of the heat exchanger 100 at a low level, enabling the heat exchanger 100 to achieve efficient heat exchange even when the second dimension Tf in the first direction x is large.

[0043] In some embodiments, see Figure 5 , Figure 6 , Figure 7 The fin 110 has multiple mounting areas 300 arranged along the first direction x, and each mounting area 300 has multiple mounting holes spaced apart along the second direction y. The mounting holes are used to install refrigerant pipes 120.

[0044] It should be noted that each installation area 300 includes multiple sub-installation areas of the same size arranged sequentially along the second direction y. Multiple mounting holes are located in their respective sub-installation areas, and the positions of the multiple mounting holes in their respective sub-installation areas are the same. Therefore, the pipe spacing 'a' of the refrigerant pipes 120 along the second direction y is the spacing between two adjacent mounting holes along the second direction y. The spacing between two adjacent mounting holes along the second direction y is equal to the size of the sub-installation area along the second direction y. Therefore, the size of the installation area 300 along the second direction y is equal to the size of the sub-installation area along the second direction y multiplied by the number of sub-installation areas along the second direction y.

[0045] The above configuration facilitates the adjustment of the size of the heat exchanger 100 along the second direction y by adjusting the pipe spacing a of the refrigerant pipe 120 along the second direction y and the number of mounting holes in each mounting area 300; it also facilitates the adjustment of the size of the heat exchanger 100 along the third direction z by adjusting the size of each mounting area 300 along the first direction x and the number of mounting areas 300 in which the fins 110 are arranged along the first direction x.

[0046] In some embodiments, the specific number or arrangement of refrigerant pipes 120 is not limited.

[0047] For example, heat exchanger 100 includes a non-welded serpentine coiled tube, which serves as refrigerant pipe 120. That is, refrigerant pipe 120 is serpentinely coiled through all the mounting holes on fin 110 to be installed on fin 110. For another example, heat exchanger 100 includes multiple serpentine coiled tubes that pass through different mounting holes on fin 110, and these multiple serpentine coiled tubes serve as multiple refrigerant pipes 120. Specifically, the coiling order of the serpentine coiled tubes is not limited, that is, the order in which the serpentine coiled tubes pass through the multiple mounting holes is not limited, and can be adjusted according to the production process or actual product requirements.

[0048] In some embodiments, the mounting holes of two adjacent mounting areas 300 are offset along the second direction y.

[0049] It should be noted that the misalignment setting refers to the projection misalignment of the mounting holes of two adjacent mounting areas 300 in a direction perpendicular to the second direction y. In some embodiments, it can be set to be completely misaligned.

[0050] Since the mounting holes are used to install the refrigerant pipes 120, and the multiple mounting areas 300 are arranged along the first direction x, when the mounting holes of two adjacent mounting areas 300 are staggered along the second direction y, which is perpendicular to the first direction x, it is easier to reduce the obstruction effect of the refrigerant pipes 120 in the mounting area 300 near the windward side on the refrigerant pipes 120 in another mounting area 300 away from the windward side, thereby improving the overall heat exchange efficiency between the airflow and the refrigerant pipes 120 of the heat exchanger 100.

[0051] In some embodiments, see Figure 5 , Figure 6 , Figure 7 The fin 110 has eight mounting areas 300 arranged along the first direction x. Each mounting area 300 has three mounting holes spaced apart along the second direction y. The mounting holes are used to install refrigerant pipes 120. The outer diameter of the refrigerant pipes 120 is 5 mm, and the pipe spacing a of the refrigerant pipes 120 along the second direction y is 19.5 mm. The dimension of the mounting area 300 along the first direction x is 11.6 mm.

[0052] In this embodiment, each installation area 300 includes three sub-installation areas of the same size arranged sequentially along the second direction y. The three mounting holes are located in the corresponding sub-installation areas, and the three mounting holes are in the same position in the corresponding sub-installation areas. Therefore, the pipe spacing 'a' of the refrigerant pipes 120 along the second direction y is the spacing between two adjacent mounting holes along the second direction y. The spacing between two adjacent mounting holes along the second direction y is equal to the size of the sub-installation area along the second direction y. Therefore, the size of the installation area 300 along the second direction y is equal to the size of the sub-installation area along the second direction y multiplied by 3.

[0053] In one application scenario, when the overall height of the drying equipment is between 895mm and 850mm, the inlet air temperature of the heat exchanger is 45℃, the inlet air humidity is 70%, and the air volume is 100m³ / h. 3 / h-140m 3With a refrigerant pipe temperature of -6°C to 35°C per hour and 3 mounting holes per installation area (300 mm), the heat exchanger's heat transfer capacity and air resistance both increase with the number of installation areas. When the number of installation areas increases to 8, the rate of increase in heat transfer capacity begins to decrease significantly. Therefore, it is preferable to have 8 installation areas, which provides sufficient heat exchanger area within a compact space to achieve the rapid drying function. Furthermore, under this configuration, the impeller can overcome the corresponding air resistance and operate normally.

[0054] The refrigerant pipe 120 can also be set to have an outer diameter of 5mm. The pipe spacing of the refrigerant pipe 120 along the second direction y is 19.5mm, the pipe length of the refrigerant pipe 120 along the third direction z is 300mm, and the dimension of the installation area 300 along the first direction x is 11.6mm.

[0055] In other embodiments, the intake air temperature may be further set to a range of 5°C to 50°C, the intake air humidity to a range of 20% to 100%, and the air volume to a range of 65 m³ / h. 3 / h to 220m 3 / h.

[0056] In another application scenario, when the heat exchanger's inlet air temperature is 45℃, the inlet air humidity is 70%, and the air volume is 100m³ / h... 3 / h-140m 3 With a refrigerant pipe temperature ranging from -6°C to 35°C per hour, and 8 installation zones 300, the heat exchanger's heat transfer capacity increases and the air resistance decreases as the number of mounting holes in each installation zone increases. However, when the number of installation zones increases to 3, the rate of increase in heat transfer capacity and the rate of decrease in air resistance both begin to decrease significantly. Therefore, it is preferable to have 3 mounting holes to maximize the heat transfer capacity of the heat exchanger 100 and minimize its air resistance.

[0057] In other embodiments, the intake air temperature may be further set to a range of 5°C to 50°C, the intake air humidity to a range of 20% to 100%, and the air volume to a range of 65 m³ / h. 3 / h to 220m 3 / h.

[0058] The beneficial effect of the above configuration is that the pipe spacing a of the refrigerant pipe 120 along the second direction y is 19.5mm, and each installation area 300 is provided with 3 installation holes for installing the refrigerant pipe 120 along the second direction y at intervals. Therefore, it is convenient to set the size of the installation area 300 along the second direction y to 58.5mm, and thus convenient to set the first dimension Hf of the heat exchanger 100 along the second direction y to 58.5mm. The size of the installation area 300 for installing the refrigerant pipe 120 along the first direction x is 11.6mm, and the fins 110 are provided with 8 installation areas 300 arranged along the first direction x. Therefore, it is convenient to set the size of the fins 110 along the first direction x to 92.8mm, and thus convenient to set the second dimension Tf of the heat exchanger 100 along the first direction x to 92.8mm. Therefore, the first dimension Hf of 58.5mm and the second dimension Tf of 92.8mm make it easier to achieve a ratio of the first dimension Hf to the second dimension Tf close to 0.63. This configuration makes it easier to significantly reduce the overall height of the heat exchanger 100, resulting in a more compact design for the entire drying equipment 10.

[0059] In one application scenario, the heat exchanger 100 includes three refrigerant pipes 120 arranged along the second direction y.

[0060] See Figure 7 The fin 110 has eight mounting areas 300 arranged along the first direction x. Each mounting area 300 has a first mounting hole, a second mounting hole, and a third mounting hole arranged at intervals along the second direction y. Therefore, the fin 110 has a total of eight first mounting holes, eight second mounting holes, and eight third mounting holes. The heat exchanger 100 includes a serpentine disc-shaped first heat exchange tube 121, a second heat exchange tube 122, and a third heat exchange tube 123. The first heat exchange tube 121, the second heat exchange tube 122, and the third heat exchange tube 123 serve as refrigerant pipes 120. The first heat exchange tube 121 is installed in the first mounting hole, the second heat exchange tube 122 is installed in the second mounting hole, and the third heat exchange tube 123 is installed in the third mounting hole. The first heat exchange tube 121, the second heat exchange tube 122, and the third heat exchange tube 123 are arranged at intervals along the second direction y, and two adjacent first mounting holes are staggered along the second direction y.

[0061] In some embodiments, the first heat exchange tube 121, the second heat exchange tube 122, and the third heat exchange tube 123 can all be single tubes without welding.

[0062] In other embodiments, see Figure 8 , Figure 9 , Figure 10The fin 110 has six mounting areas 300 arranged along the first direction x. Each mounting area 300 has four mounting holes spaced apart along the second direction y. The mounting holes are used to install refrigerant pipes 120. The outer diameter of the refrigerant pipes 120 is 5 mm, and the pipe spacing a of the refrigerant pipes 120 along the second direction y is 14.5 mm. The dimension of the mounting area 300 along the first direction x is 12.56 mm.

[0063] In one application scenario, when the overall height of the drying equipment is between 895mm and 850mm, the inlet air temperature of the heat exchanger is 45℃, the inlet air humidity is 70%, and the air volume is 100m³ / h. 3 / h-140m 3 With a refrigerant pipe temperature of -6°C to 35°C per hour and 4 mounting holes per mounting area (300 mm), the heat exchanger's heat transfer capacity and air resistance both increase with the number of mounting areas. When the number of mounting areas increases to 6, the rate of increase in heat transfer capacity begins to decrease significantly. Therefore, it is preferable to have 6 mounting areas, which provides sufficient heat exchanger area within a compact space to achieve the rapid drying function. Furthermore, under this configuration, the impeller can overcome the corresponding air resistance and operate normally.

[0064] The refrigerant pipe 120 can also be configured with an outer diameter of 5mm. The pipe spacing of the refrigerant pipe 120 along the second direction y is 14.5mm, and the installation area 300 along the first direction x is 12.56mm.

[0065] In other embodiments, the intake air temperature may be further set to a range of 5°C to 50°C, the intake air humidity to a range of 20% to 100%, and the air volume to a range of 65 m³ / h. 3 / h to 220m 3 / h.

[0066] In another application scenario, when the heat exchanger's inlet air temperature is 45℃, the inlet air humidity is 70%, and the air volume is 100m³ / h... 3 / h-140m 3 With a refrigerant pipe temperature of -6°C to 35°C per hour, and 6 installation zones 300, the heat exchanger's heat transfer capacity increases and the air resistance decreases as the number of mounting holes in each installation zone increases. However, when the number of installation zones increases to 4, the rate of increase in heat transfer capacity and the rate of decrease in air resistance both decrease significantly. Therefore, it is preferable to have 4 mounting holes to maximize the heat transfer capacity of the heat exchanger 100 and minimize its air resistance.

[0067] In other embodiments, the intake air temperature may be further set to a range of 5°C to 50°C, the intake air humidity to a range of 20% to 100%, and the air volume to a range of 65 m³ / h. 3 / h to 220m3 / h.

[0068] The beneficial effect of the above configuration is that the pipe spacing of the refrigerant pipe 120 along the second direction y is 14.5mm, and each installation area 300 is provided with 4 installation holes for installing the refrigerant pipe 120 along the second direction y at intervals. Therefore, it is convenient to set the dimension of the installation area 300 along the second direction y to 58mm, and thus convenient to set the first dimension Hf of the heat exchanger 100 along the second direction y to 58mm. The dimension of the installation area 300 for installing the refrigerant pipe 120 along the first direction x is 12.56mm, and the fins 110 are provided with 6 installation areas 300 arranged along the first direction x. Therefore, it is convenient to set the dimension of the fins 110 along the first direction x to 75.36mm, and thus convenient to set the second dimension Tf of the heat exchanger 100 along the first direction x to 75.36mm. Therefore, the first dimension Hf of 58mm and the second dimension Tf of 75.36mm make it easier to achieve a ratio of the first dimension Hf to the second dimension Tf close to 0.77. This configuration makes it easier to significantly reduce the overall height of the heat exchanger 100, resulting in a more compact design for the entire drying equipment 10.

[0069] In other embodiments, the fins may also be provided with other numbers of mounting areas arranged along the first direction (e.g., 4, 2, or 1, etc.); furthermore, the number of mounting holes spaced along the second direction in the mounting areas may be adjusted according to different product requirements (e.g., 2 mounting holes are provided in each mounting area, etc.); different mounting areas may also be provided with different numbers of mounting holes, and the specific number is not limited.

[0070] In other embodiments, the outer diameter of the refrigerant pipe may be set to other values ​​according to the actual needs of the product, and no specific limitation is made.

[0071] In other embodiments, depending on the actual needs of the product, the pipe spacing of the refrigerant pipes along the second direction and the size of the installation area along the first direction can be set to other values, without any specific limitation.

[0072] In other embodiments, similar improvements can be made to the heat exchanger, which will not be described in detail here.

[0073] This application further proposes a heat pump system 11, which includes a compressor, an evaporator 600, and a condenser 400. The evaporator 600 includes a heat exchanger 100. The compressor, condenser 400, and evaporator 600 form a refrigerant circulation channel. The evaporator 600 and condenser 400 are used to be installed in the heat exchange chamber.

[0074] The specific implementation method and working principle of the heat exchanger 100 can be found in the above embodiments, and will not be repeated here.

[0075] The refrigerant circulates within the refrigerant circulation channel, and the refrigerant can exchange heat with the external airflow through refrigerant pipes, fins, etc.

[0076] The heat pump system 11 of this application can be used in drying equipment 10. Drying equipment 10 is provided with drying chamber 200. The evaporator 600 of heat pump system 11 is arranged along the second direction y with the drying chamber 200. The heat exchange chamber where the evaporator 600 is located is connected to the drying chamber 200. The evaporator 600 and condenser 400 are located in the heat exchange chamber connected to the drying chamber 200 and can exchange heat with the airflow in the drying chamber 200. The first dimension Hf of the evaporator 600 along the second direction y is smaller than its second dimension Tf along the first direction x. The first direction x is perpendicular to the second direction y. The condenser 400 and evaporator 600 are connected in series between the outlet of the compressor and the inlet of the compressor so as to realize the circulation of refrigerant through the compressor, condenser 400 and evaporator 600.

[0077] In one application scenario, the airflow first flows through the evaporator 600 and then through the condenser 400. The humid airflow in the drying chamber 200 flows into the heat exchange cavity. When the humid airflow flows through the evaporator 600, water droplets condense on the surface of the evaporator 600, exchange heat with the evaporator 600, and are converted into dry airflow. The dry airflow flows through the condenser 400 to absorb heat and become high-temperature dry airflow. The high-temperature dry airflow flows into the drying chamber 200, realizing the heating and drying of the items to be dried during the drying process. The airflow circulation between the heat exchange cavity and the drying chamber 200, and the refrigerant circulation in the heat exchange cavity, can realize the drying of the items to be dried in the drying chamber 200.

[0078] The heat pump system 11 also includes a throttling device located between the condenser 400 and the evaporator 600. The compressor is the power source of the heat pump system 11, used to adiabatically compress the low-temperature, low-pressure refrigerant vapor from the evaporator 600 into high-temperature, high-pressure refrigerant vapor, which is then supplied to the condenser 400. The condenser 400 condenses the high-temperature, high-pressure refrigerant vapor from the compressor under isobaric conditions, dissipating heat to the heat exchange chamber, i.e., exchanging heat with the airflow in the heat exchange chamber, and the refrigerant in the condenser 400 becomes a high-pressure subcooled liquid. The high-pressure subcooled liquid from the condenser 400 is throttled by the throttling device and becomes low-temperature, low-pressure refrigerant vapor, which enters the evaporator 600 for evaporation. The low-temperature, low-pressure refrigerant vapor after throttling boils under isobaric conditions in the evaporator 600, absorbing heat from the humid heat medium (e.g., the humid airflow entering the heat exchange chamber) in the heat exchange chamber, becoming low-temperature, low-pressure refrigerant vapor, which is then sent to the compressor, and causing the water vapor in the humid heat medium in the heat exchange chamber to be condensed into condensate and discharged.

[0079] The heat pump system 11 in this embodiment includes an evaporator 600, which includes the heat exchanger 100 described above. Since the evaporator 600 and the drying chamber 200 are arranged along the second direction y, the first dimension Hf of the evaporator 600 along the second direction y is set to be smaller than its second dimension Tf along the first direction x. This makes it easier to reduce the overall size of the drying equipment 10 in the second direction y, and it is also easier to increase the total heat exchange area of ​​the evaporator 600 by increasing the second dimension Tf, thereby improving the drying efficiency of the drying equipment 10. Therefore, this arrangement can improve the structural compactness and drying efficiency of the drying equipment 10.

[0080] In some embodiments, the drying chamber 200 forms an air outlet and an air inlet communicating with the heat exchange chamber. Moist air flows from the drying chamber 200 to the heat exchange chamber through the air outlet of the drying chamber 200, and then flows to the evaporator 600. The high-temperature dry air flowing out of the condenser 400 flows from the heat exchange chamber into the drying chamber 200 through the air inlet of the drying chamber 200.

[0081] In some embodiments, the second direction y is parallel to the direction of gravity.

[0082] Since the horizontal direction is perpendicular to the direction of gravity, when it is necessary to arrange the evaporator 600 and condenser 400 in the first direction x to reduce the air resistance of the airflow entering the condenser 400 through the evaporator 600, setting the first direction x to be perpendicular to the second direction y makes it easier to arrange the evaporator 600 and condenser 400 in the horizontal direction. This not only facilitates the optimization of their layout, but also makes it easier to place the condenser 400 above the drying chamber 200. This simplifies the structural design of the heat exchange chamber and refrigerant flow channel where they are located, saves costs, and improves the reliability of their operation.

[0083] In other embodiments, the second direction may intersect with or be opposite to the direction of gravity, and there is no specific limitation.

[0084] In some embodiments, see Figure 4 , Figure 9 The heat exchanger's refrigerant pipe 120 has an inlet and an outlet, and the evaporator 600 has multiple first refrigerant pipes 1201. Figure 4 The first refrigerant pipe 1201 includes a first heat exchange pipe 121, a second heat exchange pipe 122, and a third heat exchange pipe 123. The condenser 400 is provided with a second refrigerant pipe 1202. The inlets of multiple first refrigerant pipes 1201 are all connected to the outlet of the same second refrigerant pipe 1202, and the inlets of multiple second refrigerant pipes 1202 are all connected to the outlet of the compressor.

[0085] During a complete dehumidification and heating process of the airflow, the condenser 400 needs to heat the dry airflow to make it a high-temperature dry airflow. Therefore, the heat exchange capacity of the condenser 400 is usually greater than that of the evaporator 600. Thus, the outer diameter of the second refrigerant pipe 1202 (the refrigerant pipe 120 of the condenser 400) is usually larger than that of the first refrigerant pipe 1201 (the refrigerant pipe 120 of the evaporator 600). Since the evaporator 600, condenser 400, and compressor form a connected refrigerant circulation channel, the evaporator 600 is designed to include multiple first refrigerant pipes 1201. This allows the refrigerant flowing out of the second refrigerant pipe 1202 with a larger outer diameter to be diverted when entering the first refrigerant pipe 1201 with a smaller outer diameter. This reduces the impact of the smaller outer diameter of the first refrigerant pipe 1201 on the refrigerant flow rate, thus facilitating an overall increase in the refrigerant flow rate within the heat pump system 11 and improving the overall heat exchange effect.

[0086] In some embodiments, see Figure 4 Multiple first refrigerant pipes 1201 are arranged at intervals along the second direction y.

[0087] This arrangement facilitates production and assembly, improves the simplicity of structural design, and the spacing along the second direction y facilitates the formation of gaps between multiple first refrigerant pipes 1201, which in turn facilitates airflow and improves heat exchange efficiency.

[0088] In other embodiments, the multiple first refrigerant pipes may be arranged in a cross pattern, and their winding method is not limited.

[0089] In one application scenario, heat exchanger 100 is used as an evaporator. (See also...) Figure 9 Multiple refrigerant pipes 1201 are arranged in a crisscross pattern. The refrigerant enters the evaporator and splits into two streams, flowing into two separate refrigerant pipes 1201. The flow rate in these two pipes is often uneven. The pipe with the higher flow rate carries too much refrigerant, resulting in incomplete evaporation before leaving the evaporator and wasted flow. Conversely, the other pipe carries too little refrigerant, causing premature evaporation and wasted evaporation area. By arranging multiple refrigerant pipes 1201 in a crisscross pattern, the refrigerant in the pipe with the higher flow rate can flow to the side of the pipe with the lower flow rate, achieving heat exchange and resulting in a more uniform heat exchange effect throughout the evaporator.

[0090] This application further proposes a drying device 10, which includes a drying chamber 200, an air duct shell, and a heat pump system 11. The air duct shell forms a heat exchange cavity communicating with the drying chamber 200. The heat pump system 11 includes a compressor, an evaporator 600, and a condenser 400, with at least the evaporator 600 and the condenser 400 disposed in the heat exchange cavity. The evaporator 600 and the condenser 400 are arranged in a horizontal direction, with the second direction y being the direction of gravity.

[0091] The specific implementation method and working principle of the heat pump system 11 can be found in the above embodiments, and will not be repeated here; the specific implementation method and working principle of the heat exchanger 100 can be found in the above embodiments, and will not be repeated here.

[0092] It should be noted that the drying equipment 10 of this application can be, for example, a clothes dryer, a dry cleaning machine, a dryer, or other equipment with at least a drying function; the drying chamber 200 is used to hold the items to be dried; the evaporator 600 and the condenser 400 are arranged in a horizontal direction, which means that the evaporator 600 and the condenser 400 are completely misaligned in the horizontal direction, that is, the projection of the evaporator 600 in a direction perpendicular to the horizontal direction and the projection of the condenser 400 in that direction are completely misaligned and do not overlap.

[0093] The heat exchange chamber is connected to the drying chamber 200. The evaporator 600 and condenser 400 are located in the heat exchange chamber, facilitating heat exchange between them and the drying chamber 200, improving the drying efficiency of the drying chamber 200, and reducing external environmental interference with the evaporator 600 and condenser 400, thus increasing their operating efficiency and reducing the likelihood of damage. The horizontal arrangement of the evaporator 600 and condenser 400 optimizes their layout, simplifies the structural design of the heat exchange chamber and refrigerant flow channels, saves costs, and improves their operational reliability. The arrangement of the heat exchanger 100 and the drying chamber 200 along the direction of gravity (i.e., the second direction y) also optimizes their layout. When the heat exchanger 100 is located above the drying chamber 200... In this case, this arrangement facilitates the drying chamber 200 to provide certain support for the heat exchanger 100, thereby improving the positional stability of the heat exchanger 100. The drying equipment 10 in this embodiment includes the aforementioned evaporator 600, which includes the aforementioned heat exchanger 100. Since the evaporator 600 and the drying chamber 200 are arranged along the second direction y, the first dimension Hf of the evaporator 600 along the second direction y is set to be smaller than its second dimension Tf along the first direction x. This facilitates reducing the overall size of the drying equipment 10 in the second direction y, and also facilitates increasing the total heat exchange area of ​​the evaporator 600 by increasing the second dimension Tf, thereby improving the drying efficiency of the drying equipment 10. Therefore, this arrangement can improve the structural compactness and drying efficiency of the drying equipment 10.

[0094] In some embodiments, the evaporator 600 is positioned near the air inlet of the heat exchange chamber, and the condenser 400 is positioned near the air outlet of the heat exchange chamber. The air inlet of the heat exchange chamber is connected to the air outlet of the drying chamber 200, which can optimize the structure of the entire drying equipment 10.

[0095] In some embodiments, the drying equipment 10 further includes a fan 12, which draws the humid airflow in the drying chamber 200 into the heat exchange chamber to facilitate airflow circulation between the drying chamber 200 and the heat exchange chamber.

[0096] In some embodiments, one or more of the evaporator 600, condenser 400, compressor, and fan 12 are connected to the duct housing, and the duct housing supports one or more of the evaporator 600, condenser 400, compressor, and fan 12 to improve the structural stability of the drying equipment 10, etc.

[0097] It should be noted that there is no limitation on the specific connection method between it and the air duct shell, such as fixed connection such as adhesive bonding or detachable connection.

[0098] In some embodiments, the duct housing may have an installation position outside the heat exchange chamber for mounting compressors, fans, etc.

[0099] By integrating the compressor, fan 12, condenser 400, and evaporator 600 into the air duct housing, the structural layout can be optimized, structural stability improved, and structural volume reduced.

[0100] In some embodiments, the drying chamber 200 includes a drum, an air duct shell is disposed above the drum, and an evaporator 600 and a condenser 400 are arranged sequentially along a first direction x and disposed within a heat exchange cavity formed by the air duct shell.

[0101] In some embodiments, the axial direction of the drum is perpendicular to both the first direction x and the second direction y, that is, the third direction z is parallel to the axial direction of the drum; wherein, the second direction y is the direction of gravity, the drum and the evaporator 600 are arranged along the second direction y, and the evaporator 600 is disposed above the drum; the evaporator 600 and the condenser 400 are arranged sequentially along the first direction x.

[0102] The evaporator 600 and condenser 400 are arranged along the first direction x, which facilitates the smooth flow of air through the evaporator 600 into the condenser 400, reduces airflow resistance, improves the overall heat exchange efficiency of the heat pump system 11, optimizes the structural layout, reduces size, and facilitates the placement of the fan 12 and optimizes the air duct structure. Furthermore, when the evaporator 600 and condenser 400 are arranged along the first direction x, making the first direction x perpendicular to the axis of the drum, it is easier to make full use of the space above the drum to accommodate the evaporator 600 and condenser 400. For example, the condenser 400, which has a larger heat exchange capacity, can be placed in the area diagonally above the drum with more space, thereby improving the structural compactness of the drying equipment 10 and achieving miniaturization. In other embodiments, the evaporator 600 and condenser can also be arranged in other directions, with the airflow first flowing through the evaporator 600 for dehumidification and then flowing into the condenser for heating; the specific arrangement is not limited.

[0103] In some embodiments, the condenser 400 is disposed diagonally above the drum, and the top of the condenser 400 is flush with the top of the evaporator 600. This arrangement facilitates maximizing the heat exchange space of the condenser 400, improving the heat exchange efficiency of the condenser 400, and also enhances the overall structural reliability of the drying equipment 10.

[0104] In some embodiments, the height difference between the bottom of the condenser 400 and the horizontal plane containing the geometric center of the drum decreases along the first direction x.

[0105] This design allows the bottom of the condenser 400 to fit as close as possible to the drum wall; that is, the bottom of the condenser 400 is not a flat surface, but can be stepped (see [reference]). Figure 8 The condenser 400 can be either curved or arc-shaped, which helps to maximize the heat exchange space of the condenser 400 and improve its heat exchange efficiency.

[0106] In other embodiments, the first direction may also be set to be parallel to the axis of the roller and perpendicular to the second direction, without being specifically limited.

[0107] In some embodiments, the drying device 10 further includes a baffle plate disposed on the bottom wall of the heat exchange chamber to form a water collection tank on the bottom wall. The water collection tank is used to collect liquid flowing down from the evaporator 600, such as condensate produced by the evaporator 600.

[0108] In other embodiments, the positional relationship between the drying chamber and the heat exchange chamber may not be limited.

[0109] Unlike existing technologies, the heat exchanger in this application is located in a heat exchange chamber that is connected to the drying chamber, facilitating airflow between the two chambers and improving heat exchange efficiency. The heat exchanger's placement within the heat exchange chamber reduces external environmental interference, increasing its efficiency and reducing the likelihood of damage. The arrangement of the heat exchanger and drying chamber along a second direction optimizes their layout, simplifies structural design, and enhances operational reliability. For example, when the second direction is the direction of gravity and the heat exchanger is positioned above the drying chamber, this arrangement allows the drying chamber to provide support, improving the heat exchanger's positional stability. Because the heat exchanger and drying chamber are arranged along a second direction, the first dimension of the heat exchanger along the second direction is smaller than its second dimension along the first direction, reducing the overall size of the drying equipment in the second direction and improving its structural compactness. Furthermore, increasing the second dimension allows for an increase in the total heat exchange area of ​​the heat exchanger, thereby improving the heat exchange efficiency of the heat pump system.

[0110] It is worth noting that the accompanying drawings are only for illustrating the structural and connection relationships of the product in this application, and do not limit the specific structural dimensions of the product in this application.

[0111] The above description is merely an embodiment of this application and does not limit the patent scope of this application. Any equivalent structural or procedural transformations made using the content of this application's specification and drawings, or direct or indirect applications in other related technical fields, are similarly included within the patent protection scope of this application.

Claims

1. A heat exchanger, characterized in that, For use in drying equipment, the heat exchanger has a windward side and a leeward side, the direction from the windward side to the leeward side is a first direction, the drying equipment has a drying chamber and the heat exchanger arranged along a second direction with the drying chamber, the heat exchanger is located in a heat exchange cavity that is connected to the drying chamber, and the first dimension of the heat exchanger along the second direction is smaller than the second dimension along the first direction; The first direction is perpendicular to the second direction.

2. The heat exchanger according to claim 1, characterized in that, The heat exchanger includes: Fins are provided extending along the first direction and the second direction; Refrigerant pipes are disposed on the fins; Wherein, the first dimension of the fin along the second direction is smaller than the second dimension of the fin along the first direction.

3. The heat exchanger according to claim 1 or 2, characterized in that, The ratio between the first dimension and the second dimension is 0.5 to 0.

95.

4. The heat exchanger according to claim 2, characterized in that, The heat exchanger includes a plurality of fins spaced apart along a third direction, with the spacing between adjacent fins being 1.4 mm to 2 mm; The third direction is respectively perpendicular to the first direction and the second direction.

5. The heat exchanger according to claim 4, characterized in that, The interval is 1.5 mm.

6. The heat exchanger according to claim 2, characterized in that, The fins are provided with 8 mounting areas arranged along the first direction, and each mounting area is provided with 3 mounting holes spaced apart along the second direction. The mounting holes are used to install the refrigerant pipe. The outer diameter of the refrigerant pipe is 5 mm, the pipe spacing along the second direction is 19.5 mm, and the dimension of the installation area along the first direction is 11.6 mm.

7. The heat exchanger according to claim 2, characterized in that, The fins are provided with 6 mounting areas arranged along the first direction, and each mounting area is provided with 4 mounting holes spaced apart along the second direction. The mounting holes are used to install the refrigerant pipe. The outer diameter of the refrigerant pipe is 5 mm, the pipe spacing along the second direction is 14.5 mm, and the dimension of the installation area along the first direction is 12.56 mm.

8. A heat pump system, characterized in that, The heat pump system includes: compressor; Evaporator, the evaporator comprising the heat exchanger according to any one of claims 1 to 7; The condenser, the compressor, and the evaporator form a refrigerant circulation channel; The evaporator and the condenser are arranged inside the heat exchange chamber.

9. The heat pump system according to claim 8, characterized in that, The heat exchanger has refrigerant pipes with inlets and outlets, the evaporator has multiple first refrigerant pipes, and the condenser has second refrigerant pipes. The inlets of the multiple first refrigerant pipes are all connected to the outlet of the same second refrigerant pipe, and the inlets of the multiple second refrigerant pipes are all connected to the outlet of the compressor.

10. The heat pump system according to claim 9, characterized in that, The plurality of first refrigerant pipes are arranged at intervals along the second direction.

11. A drying device, characterized in that, The drying equipment includes: Drying room; The air duct shell has a heat exchange chamber that communicates with the drying chamber; The heat pump system according to any one of claims 8 to 10, wherein at least the evaporator and the condenser are disposed in the heat exchange chamber; in, The evaporator and the condenser are arranged in a horizontal direction, and the second direction is the direction of gravity.

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