Heat pump system and drying device

Abstract

The present application provides a heat pump system and a drying device. The heat pump system comprises a compressor, an evaporator, and a condenser, the evaporator being provided with a first windward surface, the condenser being provided with a second windward surface, and the compressor, the condenser, and the evaporator forming a refrigerant circulation channel. The area of the second windward surface is greater than the area of the first windward surface, and the ratio of the area of the second windward surface to the area of the first windward surface is less than or equal to 2. According to the present application, the optimization of the internal structural layout of the heat pump system can be facilitated, thereby improving the heat exchange efficiency of the heat pump system.

Description

Heat pump systems and drying equipment

[0001] This application claims priority to Chinese Utility Model Patent Application No. 2024227191374, filed on November 7, 2024, entitled "A Heat Pump System and Drying Equipment", and Chinese Invention Patent Application No. 2024115869282, filed on November 7, 2024, entitled "A Heat Pump System and Drying Equipment", both of which are incorporated herein by reference in their entirety. [Technical Field]

[0002] This application relates to the field of household appliance technology, and in particular to a heat pump system and drying equipment. [Background Technology]

[0003] 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. However, in existing technologies, common heat pump systems have relatively low heat exchange efficiency, and their internal structures need further optimization. [Summary of the Invention]

[0004] This application provides a heat pump system and drying equipment, which can facilitate the optimization of the internal structural layout of the heat pump system and improve the heat exchange efficiency of the heat pump system.

[0005] To solve the above-mentioned technical problems, this application provides a heat pump system, which includes a compressor, an evaporator, and a condenser. The evaporator has a first air-facing surface; the condenser has a second air-facing surface, and the compressor, condenser, and evaporator form a refrigerant circulation channel; wherein the area of ​​the second air-facing surface is larger than the area of ​​the first air-facing surface, and the ratio between the area of ​​the second air-facing surface and the area of ​​the first air-facing surface is less than or equal to 2.

[0006] To solve the above-mentioned technical problems, this application further provides a drying device, wherein the drying device includes a drying chamber, an air duct shell, and the aforementioned heat pump system; the air duct shell forms a heat exchange chamber communicating with the drying chamber; at least an evaporator and a condenser are disposed in the heat exchange chamber.

[0007] The beneficial effects of this application are as follows: the area of ​​the second windward surface of the condenser is larger than the area of ​​the first windward surface of the evaporator, and the ratio between the area of ​​the second windward surface and the area of ​​the first windward surface is less than or equal to 2. This facilitates increasing the heat exchange efficiency of the condenser by increasing its windward area, thereby improving the heat exchange efficiency of the heat pump system. Furthermore, increasing the windward area of ​​the condenser to increase its heat exchange efficiency facilitates optimizing the size of the condenser in the windward direction, which in turn facilitates optimizing the internal structural layout of the heat pump system. Moreover, increasing the windward area of ​​the condenser to increase its heat exchange efficiency reduces the risk of insufficient heat exchange due to an excessively large size of the condenser in the windward direction, thereby improving the overall heat exchange efficiency. [Attached Image 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 is a structural schematic diagram of an embodiment of the drying equipment of this application;

[0010] Figure 2 is a side view of the embodiment in Figure 1;

[0011] Figure 3 is a cross-sectional structural diagram of the embodiment in Figure 2;

[0012] Figure 4 is a structural schematic diagram of an embodiment of the evaporator of this application;

[0013] Figure 5 is a structural schematic diagram of an embodiment of the condenser of this application;

[0014] Figure 6 is a structural schematic diagram of an embodiment of the heat pump system of this application;

[0015] Figure 7 is a side view of the embodiment in Figure 6;

[0016] Figure 8 is a structural schematic diagram of an embodiment of the evaporator of this application;

[0017] Figure 9 is a structural schematic diagram of an embodiment of the condenser of this application;

[0018] Figure 10 is a structural schematic diagram of an embodiment of the evaporator and condenser of this application.

Detailed Implementation Methods

[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, 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, unless the context clearly indicates otherwise, the singular forms "a," "an," and "the" are intended to include the plural forms. It should also be further understood that the term "and / or," as used in this specification, refers to any combination and all possible combinations of one or more of the associated listed items, and includes such combinations.

[0021] As used in this specification, the term "if" may be interpreted, depending on the context, as "when," "once," "in response to determination," or "in response to detection." Similarly, the phrase "if determination" or "if [the described condition or event] is detected" may be interpreted, depending on the context, as "once determination," "in response to determination," "once [the described condition or event] is detected," or "in response to detection of [the described condition or event]."

[0022] 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.

[0023] 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.

[0024] This application first proposes a heat pump system 11, as shown in Figures 1 to 10. The heat pump system 11 includes a compressor, an evaporator 100, and a condenser 400. The evaporator 100 has a first air-facing surface; the condenser 400 has a second air-facing surface, and the compressor, condenser 400, and evaporator 100 form a refrigerant circulation channel; wherein the area of ​​the second air-facing surface is larger than the area of ​​the first air-facing surface, and the ratio between the area of ​​the second air-facing surface and the area of ​​the first air-facing surface is less than or equal to 2.

[0025] The heat pump system 11 of this application can be used in drying equipment 10. For example, the heat pump system 11 of this application can be used to dry humid airflow. The refrigerant circulates in the refrigerant circulation channel and the refrigerant can exchange heat with the external airflow through refrigerant pipes, fins and the like.

[0026] It should be noted that the area of ​​the second windward surface of the condenser 400 is greater than the area of ​​the first windward surface of the evaporator 100. That is, when the airflow passes through the evaporator 100 or the condenser 400, the windward area of ​​the condenser 400 is greater than the windward area of ​​the evaporator 100, and the ratio of the windward area of ​​the condenser 400 to the windward area of ​​the evaporator 100 is less than or equal to 2.

[0027] In this application, the area of ​​the second windward surface of the condenser 400 is larger than the area of ​​the first windward surface of the evaporator 100, and the ratio between the area of ​​the second windward surface and the area of ​​the first windward surface is less than or equal to 2. This facilitates increasing the heat exchange efficiency of the condenser 400 by increasing its windward area, thereby improving the heat exchange efficiency of the heat pump system 11. Furthermore, increasing the windward area of ​​the condenser 400 to increase its heat exchange efficiency facilitates optimizing the size of the condenser 400 in the windward direction, which in turn facilitates optimizing the overall structural layout of the heat pump system 11. Moreover, increasing the windward area of ​​the condenser 400 to increase its heat exchange efficiency reduces the risk of insufficient heat exchange due to an excessively large size of the condenser 400 in the windward direction, thereby improving the overall heat exchange efficiency.

[0028] In one application scenario, as shown in Figures 4 and 5, the direction from the first windward side of the evaporator 100 to the leeward side of the evaporator 100 is the first direction x. The first direction x is perpendicular to the second direction y and the third direction z. The evaporator 100 includes a plurality of first fins 110 arranged at intervals along the third direction z, and the condenser 400 includes a plurality of second fins 410 arranged at intervals along the third direction z. The first fins 110 and the second fins 410 extend along the second direction y and the first direction x to form their respective main heat exchange surfaces. The area of ​​the first windward side is equal to the product of the distance Lf between the two farthest first fins 110 and the size Hf of the first fin 110 in the second direction y. The area of ​​the second windward side is equal to the product of the distance Lf between the two farthest second fins 410 and the size Hf of the second fin 410 in the second direction y.

[0029] In one application scenario, referring to Figures 2 and 6, the airflow first flows through the evaporator 100 and then through the condenser 400; the drying equipment 10 includes a drying chamber 200 connected to the heat exchange cavity, the drying chamber 200 being used to hold the object to be dried, and the evaporator 100 and condenser 400 being disposed within the heat exchange cavity (in some embodiments, they may be disposed within the same air duct); the condenser 400 and evaporator 100 are connected in series between the outlet and inlet of the compressor to achieve refrigerant circulation through the compressor, condenser 400, and evaporator 100; Moist airflow in the dry chamber 200 flows into the heat exchange chamber. As the moist airflow passes through the evaporator 100, water droplets condense on the surface of the evaporator 100, exchanging heat with the evaporator 100 and converting into dry airflow. The dry airflow passes through the condenser 400, absorbs heat, and becomes 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 chamber and the drying chamber 200, and the refrigerant circulation in the heat exchange chamber, can realize the drying of the items to be dried in the drying chamber 200.

[0030] The heat pump system 11 also includes a throttling device located between the condenser 400 and the evaporator 100. 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 100 into high-temperature, high-pressure refrigerant vapor and supply it to the condenser 400. The condenser 400 condenses the high-temperature, high-pressure refrigerant vapor from the compressor under isobaric conditions and dissipates heat to the heat exchange chamber, that is, it exchanges 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 100 for evaporation. The low-temperature, low-pressure refrigerant wet vapor after throttling boils in the evaporator 100 under isobaric conditions, absorbs heat from the humid heat medium (such as the humid airflow entering the heat exchange chamber) in the heat exchange chamber, and becomes low-temperature, low-pressure refrigerant vapor to the compressor, and causes the water vapor in the humid heat medium in the heat exchange chamber to be condensed into condensate and discharged.

[0031] During normal operation of the heat pump system 11, such as in 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 100. In the prior art, it is usually necessary to increase the total heat exchange space of the condenser 400 by increasing the number of refrigerant pipes in the condenser 400, thereby increasing the heat exchange efficiency of the condenser 400. However, how to further optimize the overall size of the condenser 400 to further improve its heat exchange efficiency is an important issue that has been of great concern to those skilled in the art.

[0032] Generally, the arrangement or winding method of the refrigerant pipes will affect the overall size of the condenser 400. However, if the number of rows of refrigerant pipes in the first direction x is blindly increased, the overall size of the condenser 400 in the first direction x will be too large, resulting in insufficient heat exchange and low heat exchange efficiency.

[0033] The area of ​​the second windward surface of the condenser 400 is larger than the area of ​​the first windward surface of the evaporator 100. This makes it easier to increase the heat exchange efficiency of the condenser 400 by increasing its windward area. Therefore, it is easier to further optimize the dimensions of the condenser 400 along the first direction x, thereby reducing the risk of insufficient heat exchange caused by the condenser 400 being too long along the first direction x, and improving the heat exchange efficiency of the condenser 400.

[0034] In some embodiments, the ratio is greater than or equal to 1.05.

[0035] Setting the ratio between the area of ​​the second windward surface and the area of ​​the first windward surface to be greater than or equal to 1.05 can improve the heat exchange efficiency of the condenser 400, thereby making it more energy-efficient.

[0036] In some embodiments, the ratio can be 1.05, 1.08, 1.1, 1.13, 1.2, 1.25, 1.34, 1.4, 1.45, 1.5, 1.52, 1.6, 1.7, 1.78, 1.8, 1.9 or 2, depending on the actual needs of the product.

[0037] In one application scenario, based on simulation results, using this heat pump system in a drying equipment can reduce drying time by 20%, lower duct resistance, and achieve a drying range of 100m. 3 / h-140m 3 / h airflow; and the above improvements to the heat pump system can effectively improve space utilization, making the product design more reasonable and compact; the above methods can also reduce the temperature of the heat pump system, keeping the maximum temperature of the entire heat pump system below 90℃, thus improving safety.

[0038] In other embodiments, the ratio may also be set to other values ​​greater than 1, such as 1.04 or 1.038, without any specific limitation.

[0039] In some embodiments, the direction from the first windward side to the leeward side of the evaporator 100 is the first direction x, and the projection of the evaporator 100 toward the first direction x is located within the projection of the condenser 400 toward the first direction x.

[0040] The first direction x is the direction in which the airflow passes through the evaporator 100. This setting facilitates the airflow to flow directly into the condenser 400 after passing through the evaporator 100, which simplifies the air duct structure and reduces air resistance.

[0041] In some embodiments, the first fins 110 of the evaporator 100 are provided with a plurality of first mounting regions 130 arranged along a first direction x, and the first mounting regions 130 are used to mount the first refrigerant pipe 120 of the evaporator 100; the second fins 410 of the condenser 400 are provided with a plurality of second mounting regions 430 arranged along a first direction x, and the second mounting regions 430 are used to mount the second refrigerant pipe 420 of the condenser 400; wherein, the outer diameter of the first refrigerant pipe 120 is smaller than the outer diameter of the second refrigerant pipe 420, and the number of first mounting regions 130 is greater than the number of second mounting regions 430.

[0042] For example, referring to Figures 8 and 9, in some application scenarios, the outer diameter of the first refrigerant pipe 120 is 5mm, and the outer diameter of the second refrigerant pipe 420 is 7mm; in some application scenarios, the number of first installation areas 130 is 8, and the number of second installation areas 430 is 3, 4, 5, or 6; in some application scenarios, each first installation area 130 includes 3 first installation holes arranged along the second direction y, and the first installation holes are used to install the first refrigerant pipe 120; in some application scenarios, each second installation area 430 includes 4 second installation holes arranged along the second direction y, and the second installation holes are used to install the second refrigerant pipe 420; in other embodiments, the specific number and size of the installation holes, the specific number and size of the installation areas, etc., can be adjusted according to product design requirements.

[0043] The beneficial effect of the above configuration is that the first fin 110 is provided with a plurality of first mounting areas 130 arranged along the first direction x, and the second fin 410 is provided with a plurality of second mounting areas 430 arranged along the first direction x. This facilitates the adjustment of the size of the evaporator 100 or the condenser 400 along the first direction x by adjusting the size of each first mounting area 130 or second mounting area 430 along the first direction x and the number of first mounting areas 130 or second mounting areas 430 arranged along the first direction x.

[0044] Furthermore, since the heat exchange capacity of the condenser 400 is usually greater than that of the evaporator 100, setting the outer diameter of the first refrigerant pipe 120 to be smaller than the outer diameter of the second refrigerant pipe 420 facilitates the realization that the heat exchange capacity of the condenser 400 is greater than that of the evaporator 100. Furthermore, in order to avoid the drying equipment 10 being too large in the second direction y (for example, in an application scenario, the evaporator 100 is used for the drying equipment 10, and the drying chamber 200 of the drying equipment 10 and the evaporator 100 are arranged in the second direction y perpendicular to the first direction x), the size of the evaporator 100 in the second direction y should not be too large. Therefore, the number of first installation areas 130 of the evaporator 100 is set to be greater than the number of second installation areas 430 of the condenser 400. The heat exchange space of the evaporator 100 can be increased by increasing the size of the evaporator 100 in the first direction x, thereby improving the heat exchange effect of the evaporator 100 and avoiding an excessively large difference in heat exchange capacity between the evaporator 100 and the condenser 400.

[0045] In some embodiments, referring to Figures 3, 4, and 5, the dimension of the condenser 400 along the first direction x is smaller than the dimension of the evaporator 100 along the first direction x, and the spacing Fp between the first fins 110 of adjacent evaporators 100 is greater than the spacing Fp between the second fins 410 of adjacent condensers 400.

[0046] Specifically, the evaporator 100 includes a plurality of first fins 110 spaced apart along a third direction z perpendicular to the first direction x, and the condenser 400 includes a plurality of second fins 410 spaced apart along a third direction z perpendicular to the first direction x; the distance Fp between two adjacent first fins 110 along the third direction z is greater than the distance Fp between two adjacent second fins 410 along the third direction z; for example, the distance Fp between adjacent first fins 110 is 1.5 mm, and the distance Fp between adjacent second fins 410 is 1.2 mm. Other values ​​may be used in other embodiments, which will not be elaborated here.

[0047] To improve the overall structural compactness of the drying equipment 10 and optimize its layout, and to reduce the risk of insufficient heat exchange due to excessive length of the condenser 400 along the first direction x, the dimension of the condenser 400 along the first direction x is set to be smaller than that of the evaporator 100 along the first direction x (for example, when the evaporator 100 and the condenser 400 are arranged along the first direction x, this design can reduce the dimension of the drying equipment 10 in the first direction x). Since the heat exchange capacity of the condenser 400 in the heat pump system 11 is usually greater than that of the evaporator 100, in order to improve the heat exchange efficiency of the condenser 400, the distance Fp between two adjacent first fins 110 can be set to be greater than the distance Fp between two adjacent second fins 410, that is, the distribution of the second fins 410 of the condenser 400 is more dense, thus facilitating the condenser 400 to set more second fins 410 in the third direction z, thereby improving the heat exchange efficiency of the condenser 400.

[0048] In some embodiments, the area of ​​the first windward surface can be adjusted by adjusting the size of the evaporator 100 in the third direction z. For example, the spacing Fp between two adjacent first fins 110 in the third direction z and the number of first fins 110 can be adjusted to adjust the spacing between the two first fins 110 with the farthest spacing in the third direction z, thereby adjusting the area of ​​the first windward surface. Similarly, similar improvements can be made to the second fin 410 and the condenser to adjust the area of ​​the second windward surface.

[0049] This application further proposes a drying device 10, referring to Figures 1 to 10. The drying device 10 includes a drying chamber 200, an air duct shell 13, and the aforementioned heat pump system 11. The air duct shell 13 forms a heat exchange chamber communicating with the drying chamber 200. At least an evaporator 100 and a condenser 400 are disposed in the heat exchange chamber.

[0050] It should be noted that the drying equipment 10 of 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 of this application can be a separate drying chamber 200 or a washer-dryer, and is not specifically limited.

[0051] 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.

[0052] The heat exchange chamber is connected to the drying chamber 200. The evaporator 100 and condenser 400 are located in the heat exchange chamber, which facilitates heat exchange between the evaporator 100 and condenser 400 and the drying chamber 200, improves the drying efficiency of the drying chamber 200, and reduces the interference of the external environment on the evaporator 100 and condenser 400, thereby improving their working efficiency and reducing the probability of damage. Furthermore, the use of the aforementioned heat pump system 11 in the drying equipment 10 facilitates the improvement of the drying efficiency of the drying equipment 10 and makes the drying equipment 10 more energy-efficient.

[0053] In some embodiments, the drying chamber 200 and the evaporator 100 are arranged along the second direction y.

[0054] It should be noted that the arrangement of the drying chamber 200 and the evaporator 100 along the second direction y means that the projection of the evaporator 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, the projection refers to the orthographic projection.

[0055] Arranging the drying chamber 200 and the evaporator 100 along the second direction y can optimize their layout, simplify the structural design, and improve the reliability of their operation. For example, when the second direction y is parallel to the direction of gravity and the evaporator 100 is located above the drying chamber 200, this arrangement makes it easier for the drying chamber 200 to provide certain support for the evaporator 100, thereby improving the positional stability of the evaporator 100.

[0056] In some embodiments, in order to further optimize the structural layout of the drying equipment 10, the evaporator 100 and the condenser 400 are arranged along the first direction x.

[0057] It should be noted that the arrangement of evaporator 100 and condenser 400 along the first direction x means that the projections of evaporator 100 and condenser 400 in the direction perpendicular to the first direction x do not overlap or are misaligned.

[0058] The evaporator 100 and condenser 400 are arranged along the first direction x, which facilitates the smooth entry of the airflow through the evaporator 100 into the condenser 400, reduces the flow resistance of the airflow, improves the heat exchange efficiency of the heat pump system 11, optimizes the structural layout, reduces the size, and facilitates the setting of the fan 12 position and optimizes the air duct structure.

[0059] In some embodiments, the second direction y is perpendicular to the first direction x. This facilitates the guidance of airflow into the evaporator 100 and reduces the interference of the drying chamber 200 on airflow guidance.

[0060] In one application scenario, when the second direction y is parallel to the direction of gravity, since the horizontal direction is perpendicular to the direction of gravity, when it is necessary to arrange the evaporator 100 and condenser 400 in the first direction x to reduce the air resistance of the airflow entering the condenser 400 through the evaporator 100, setting the first direction x to be perpendicular to the second direction y makes it easier to arrange the evaporator 100 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.

[0061] In some embodiments, the third direction z is perpendicular to both the first direction x and the second direction y.

[0062] Since the second direction y is the arrangement direction of the drying chamber 200 and the evaporator 100, the multiple first fins 110 are arranged along the third direction z, which is perpendicular to the second direction y. This facilitates the straight pipe section of the first refrigerant pipe 120 provided on the first fins 110 to extend along the third direction z, which in turn facilitates the straight pipe section of the first refrigerant pipe 120 to extend along the wall of the drying chamber 200. Since the straight pipe section is provided on the first fins 110, this arrangement facilitates the reduction of the gap between the first fins 110 and the wall of the drying chamber 200, improves the structural compactness between the evaporator 100 and the drying chamber 200, and facilitates the fixation of the position of the evaporator 100. Similarly, the multiple second fins 410 arranged along the third direction z, which is perpendicular to the second direction y, can improve the structural compactness and positional stability between the condenser 400 and the drying chamber 200.

[0063] In some embodiments, the drying chamber 200 includes a drum, the axis of which is perpendicular to both the first direction x and the second direction y. The first direction x is the direction from the first windward side of the evaporator 100 to the leeward side of the evaporator 100. The evaporator 100 and the condenser 400 are arranged along the first direction x. The second direction y is the arrangement direction of the evaporator 100 and the drum.

[0064] It should be noted that the axis of the drum is set perpendicular to both the first direction x and the second direction y, and therefore the axis of the drum is set parallel to the third direction z. The fact that the axis of the drum is perpendicular to both the first direction x and the second direction y means that the axis of the drum is perpendicular to the direction from the first windward side of the evaporator 100 to the leeward side of the evaporator 100, and the axis of the drum is perpendicular to the arrangement direction of the evaporator 100 and the drum. Furthermore, the fact that the axis of the drum is perpendicular to the arrangement direction of the evaporator 100 and the drum means that the evaporator 100 and the drum are arranged radially along the drum.

[0065] The beneficial effects of the above arrangement are that the evaporator 100 and the condenser 400 are arranged along the first direction x, which makes it easier to reduce the air resistance of the airflow from the evaporator 100 to the condenser 400; the axis of the drum is set perpendicular to both the first direction x and the second direction y, which makes it easier to arrange the evaporator 100 and the condenser 400 along the circumference of the drum, which makes it easier to reserve more installation space for the condenser 400, and can improve the structural compactness of the drying equipment 10.

[0066] In some embodiments, the first direction x is perpendicular to the second direction y.

[0067] Since the evaporator 100 and condenser 400 are arranged along the first direction x, and the first direction x is perpendicular to the second direction y, the arrangement direction of the evaporator 100 and condenser 400 is perpendicular to the arrangement direction of the evaporator 100 and the drum. This arrangement allows for better positioning of the condenser 400, makes full use of the space around the drum, and facilitates increasing the size of the condenser 400 in the arrangement direction of the evaporator 100 and the drum (i.e., the second direction y). This makes it easier to make the size of the condenser 400 along the second direction y larger than that of the evaporator 100, thereby increasing the air-facing area of ​​the condenser 400, making the area of ​​the second air-facing surface larger than that of the first air-facing surface, and improving the heat exchange capacity of the condenser 400.

[0068] In other embodiments, the axis of the roller may not be perpendicular to the first direction, or the first direction may not be perpendicular to the second direction. This can be adjusted according to the actual use requirements of the product, and will not be elaborated here.

[0069] In some embodiments, the drying chamber 200 includes a drum, with the evaporator 100 located above the drum when the axis of the drum is parallel to the horizontal plane, and the perpendicular line from the condenser 400 to the axis of the drum is set at an acute or obtuse angle to the direction of gravity of the drum.

[0070] It should be noted that this embodiment describes a scenario where the drum is positioned so that its axis is parallel to the horizontal plane, with the evaporator 100 positioned directly above the drum (making it easy to see that the arrangement direction of the evaporator 100 and the drum is parallel to the direction of gravity). The perpendicular line from the condenser 400 to the axis of the drum forms an acute or obtuse angle with the direction of gravity of the drum. When the drum's arrangement needs to be adjusted, the positions of the evaporator 100 and the condenser 400 can be changed accordingly. When the drum's axis is parallel to the horizontal plane, the evaporator 100 is positioned directly above the drum, meaning the arrangement direction of the evaporator 100 and the drum is parallel to the direction of gravity, i.e., the second direction y is parallel to the direction of gravity. The perpendicular line from the condenser 400 to the axis of the drum forms an acute or obtuse angle with the direction of gravity of the drum, meaning the condenser 400 is further away from the axis of the drum (for example, it can be positioned diagonally above the drum).

[0071] When the axis of the drum is parallel to the horizontal plane, the evaporator 100 is positioned directly above the drum, which allows the drum to provide some support for the evaporator 100 or the condenser 400, thus improving the positional stability of the evaporator 100 or the condenser 400. When the axis of the drum is parallel to the horizontal plane, the perpendicular line from the condenser 400 to the axis of the drum is set at an acute or obtuse angle with the direction of gravity of the drum. This allows for more space to be reserved for the condenser 400 (especially when the internal space of the drying equipment 10 is usually cubic or cuboid), maximizing the size of the condenser 400 in the direction of gravity. This makes it easier for the size of the condenser 400 to be larger than that of the evaporator 100 along the direction of gravity, thereby increasing the windward area of ​​the condenser 400. This also makes it easier to achieve a second windward surface area that is larger than the first windward surface area, thus improving the heat exchange capacity of the condenser 400.

[0072] In other embodiments, the evaporator may be positioned directly below the drum, while the condenser may be positioned diagonally below the drum. The specific configuration can be determined based on the actual usage requirements of the product and is not limited thereto.

[0073] In some embodiments, the axis of the drum is parallel to the horizontal plane, the side of the condenser 400 away from the drum and the side of the evaporator 100 away from the drum are located in the same horizontal plane, the height difference between the side of the condenser 400 near the drum and the center point of the drum is less than the height difference between the side of the evaporator 100 near the drum and the center point of the drum; the first direction x is perpendicular to the second direction y.

[0074] It should be noted that since the evaporator 100 and the condenser 400 are arranged along the first direction x, and the first direction x is perpendicular to the second direction y, the arrangement direction of the evaporator 100 and the condenser 400 is perpendicular to the arrangement direction of the evaporator 100 and the drum.

[0075] In one application scenario, the evaporator 100 is positioned directly above the drum, and the condenser 400 is positioned diagonally above the drum. The side of the condenser 400 facing away from the drum is on the same horizontal plane as the side of the evaporator 100 facing away from the drum. This allows the dimension of the condenser 400 along the second direction y to be larger than that of the evaporator 100, maximizing the heat exchange space of the condenser 400. Furthermore, having the side of the condenser 400 facing away from the drum and the side of the evaporator 100 facing away from the drum on the same horizontal plane improves the overall aesthetics of the structure. Further, the height difference between the side of the condenser 400 near the drum and the center point of the drum is less than the height difference between the side of the evaporator 100 near the drum and the center point of the drum. This allows the extension dimension of the condenser 400 in a plane perpendicular to the drum axis to be greater than that of the evaporator 100 in the same plane. Therefore, it facilitates setting the area of ​​the second windward surface of the condenser 400 to be larger than the area of ​​the first windward surface of the evaporator 100.

[0076] In some embodiments, the diameter of the drum is 540 mm to 570 mm, the distance between the evaporator 100 and the condenser 400 along the first direction x is 5 mm to 35 mm, the height difference between the side of the evaporator 100 near the drum and the side of the condenser 400 near the drum along the second direction y is 3 mm to 60 mm, and the first direction x is perpendicular to the second direction y.

[0077] Specifically, the diameter of the roller can be 540mm, 542mm, 545mm, 546mm, 548mm, 550mm, 553mm, 555mm, 557mm, 560mm, 565mm, 568mm or 570mm, etc., which can be adjusted according to the product's usage requirements; of course, other values ​​can also be used in other embodiments.

[0078] Specifically, the distance between the evaporator 100 and the condenser 400 along the first direction x can be set to 5mm, 6mm, 8mm, 10mm, 12mm, 15mm, 17mm, 18.5mm, 20mm, 25mm, 28mm, 30mm, 32mm or 35mm, etc., which can be adjusted according to the usage requirements of the product; of course, other values ​​can be used in other embodiments.

[0079] In one application scenario, when the axis of the drum is parallel to the horizontal plane, the axis of the drum is perpendicular to both the first direction x and the second direction y. The evaporator 100 is located directly above the drum, that is, the arrangement direction of the evaporator 100 and the drum (i.e., the second direction y) is parallel to the direction of gravity. Since the first direction x is perpendicular to the second direction y and the axis of the drum, the first direction x is parallel to the horizontal direction. The larger the distance between the evaporator 100 and the condenser 400 along the first direction x, the easier it is to increase the distance between the axis of the drum and the condenser 400 in the first direction x. Since the farther away from the axis of the drum in the first direction x, the smaller the size of the drum in the direction of gravity, the easier it is to increase the size of the condenser 400 in the direction of gravity, thus making it easier to increase the area of ​​the second windward surface of the condenser 400. The smaller the distance between the evaporator 100 and the condenser 400 along the first direction x, the easier it is to make the projection of the condenser 400 at least partially coincide with the projection of the drum in the direction of gravity, thereby making it easier to improve the structural compactness of the drying equipment 10.

[0080] Therefore, setting the distance between the evaporator 100 and the condenser 400 along the first direction x to be 5mm to 35mm not only provides sufficient installation space for the condenser 400 to a certain extent, making full use of the space around the drum, and facilitating the increase of the area of ​​the second windward surface of the condenser 400; but also improves the compactness of the overall structure.

[0081] Specifically, the height difference along the second direction y between the side of the evaporator 100 near the drum and the side of the condenser 400 near the drum can be 3mm, 5mm, 8mm, 10mm, 13mm, 15mm, 17mm, 19mm, 20mm, 25mm, 28mm, 30mm, 35mm, 36mm, 38mm, 40mm, 43mm, 45mm, 47mm, 49mm, 50mm, 52mm, 55mm, 58mm, or 60mm, etc., and can be adjusted according to the product's usage requirements; of course, other values ​​can also be used in other embodiments. This height difference refers to the distance between the side of the evaporator 100 near the drum and the side of the condenser 400 near the drum in the second direction y.

[0082] In one application scenario, when the axis of the drum is parallel to the horizontal plane, the axis of the drum is perpendicular to both the first direction x and the second direction y. The evaporator 100 is located directly above the drum, that is, the arrangement direction of the evaporator 100 and the drum (i.e. the second direction y) is parallel to the direction of gravity. This height difference refers to the height difference between the bottom of the evaporator 100 and the bottom of the condenser 400 in the second direction y (i.e. the direction of gravity).

[0083] For example, when the diameter of the drum changes, the distance between the evaporator 100 and the condenser 400 along the first direction x, and the height difference between the side of the evaporator 100 near the drum and the side of the condenser 400 near the drum along the second direction y can be modified accordingly to optimize the size of the evaporator 100 or the condenser 400, thereby optimizing the heat exchange effect.

[0084] In some embodiments, the diameter of the drum is 540 mm to 570 mm, the height difference between the side of the evaporator 100 near the drum and the center point of the drum is 270 mm to 315 mm, and the height difference between the side of the condenser 400 near the drum and the center point of the drum is 210 mm to 267 mm; the first direction x is perpendicular to the second direction y.

[0085] Specifically, the height difference between the side of the evaporator 100 near the drum and the center point of the drum can be 270mm, 275mm, 278mm, 279mm, 300mm, 305mm, 308mm, 310mm, 313mm, 314mm or 315mm, etc. This height difference refers to the distance between the side of the evaporator 100 near the drum and the center point of the drum in the second direction y, and can be adjusted according to the usage requirements of the product.

[0086] In one application scenario, when the axis of the drum is parallel to the horizontal plane, and the axis of the drum is perpendicular to both the first direction x and the second direction y, and the evaporator 100 is located directly above the drum and the condenser 400 is located diagonally above the drum, it is easy to see that the second direction y is parallel to the direction of gravity. The height difference between the side of the evaporator 100 near the drum and the center point of the drum refers to the height difference between the bottom of the evaporator 100 and the center point of the drum in the second direction y (i.e., the direction of gravity).

[0087] Of course, other values ​​can be used in other embodiments. For example, when the diameter of the drum changes, the height difference between the side of the evaporator 100 near the drum and the center point of the drum, and the height difference between the side of the condenser 400 near the drum and the center point of the drum can be modified accordingly to optimize the size of the evaporator 100 or the condenser 400, thereby optimizing the heat exchange effect.

[0088] Specifically, the height difference between the side of the condenser 400 near the drum and the center point of the drum can be 210mm, 215mm, 218mm, 220mm, 222mm, 225mm, 228mm, 230mm, 233mm, 235mm, 238mm, 240mm, 243mm, 245mm, 248mm, 250mm, 251mm, 252mm, 255mm, 258mm, 260mm, 263mm, 265mm, or 267mm, etc. This height difference refers to the distance between the side of the condenser 400 near the drum and the center point of the drum in the second direction y, and can be adjusted according to the usage requirements of the product; of course, other values ​​can also be used in other embodiments.

[0089] In one application scenario, when the axis of the drum is parallel to the horizontal plane, and the axis of the drum is perpendicular to both the first direction x and the second direction y, and the evaporator 100 is located directly above the drum and the condenser 400 is located diagonally above the drum, it is easy to see that the second direction y is parallel to the direction of gravity. The height difference between the side of the condenser 400 near the drum and the center point of the drum refers to the height difference between the bottom of the condenser 400 and the center point of the drum in the second direction y (i.e., the direction of gravity).

[0090] The above settings facilitate the improvement of the overall compactness of the drying equipment 10.

[0091] In some embodiments, referring to FIG3, the heat pump system 11 further includes a fan 12, which is disposed at the air outlet of the air duct housing 13 to guide the gas in the heat exchange chamber into the drying chamber 200. The fan 12 is located on the side of the condenser 400 away from the evaporator 100, and the height difference between the bottom of the condenser 400 and the fan shaft 123 of the fan 12 is -10mm to 30mm.

[0092] The fan 12 is used to promote airflow circulation in the heat exchange chamber and the drying chamber 200. The fan 12 is located on the side of the condenser 400 away from the evaporator 100, which facilitates the optimization of the structural design. It can make its air inlet connected to the heat exchange chamber and its air outlet connected to the drying chamber, so that the fan 12 can guide the airflow from the evaporator 100 to the condenser 400, and then guide the airflow from the condenser 400 to the drying chamber 200.

[0093] It should be noted that the height difference between the bottom of the condenser 400 and the fan shaft 123 of the fan 12 refers to the value obtained by subtracting the height of the fan shaft of the fan 12 from the height of the bottom of the condenser 400 in the arrangement direction of the evaporator 100 and the drum (i.e., the second direction y). This value can be negative, meaning that the height of the bottom of the condenser 400 in the second direction y can be less than the height of the fan shaft 123 of the fan 12; when the value is positive, it means that the height of the bottom of the condenser 400 in the second direction y can be higher than the height of the fan shaft 123 of the fan 12.

[0094] For example, in one application scenario, when the axis of the drum is parallel to the horizontal plane, and the axis of the drum is perpendicular to both the first direction x and the second direction y, and the evaporator 100 is located directly above the drum and the condenser 400 is located diagonally above the drum, it is easy to see that the arrangement direction of the evaporator 100 and the drum is parallel to the direction of gravity, that is, the second direction y is parallel to the direction of gravity. Therefore, the height difference between the bottom of the condenser 400 and the fan shaft 123 of the fan 12 refers to the height difference between the bottom of the condenser 400 and the fan shaft 123 of the fan 12 in the direction of gravity.

[0095] Specifically, the height difference between the bottom of the condenser 400 and the fan shaft 123 of the fan 12 can be -10mm, -9mm, -8mm, -5mm, -2mm, 0mm, 1mm, 3mm, 5mm, 6mm, 8mm, 9mm, 10mm, 15mm, 20mm, 23mm, 25mm, 26mm, 27mm, 29mm, or 30mm, etc., which can be adjusted according to the usage requirements of the product; of course, other values ​​can also be used in other embodiments.

[0096] In other embodiments, the duct structure and fan position can be adjusted as needed. For example, the fan can be located on the side of the evaporator away from the condenser, with the fan outlet connected to the heat exchange chamber and the fan inlet connected to the drying chamber.

[0097] In some embodiments, the heat pump system 11 further includes a fan 12, which is disposed at the air outlet of the air duct housing 13 to guide the gas in the heat exchange chamber into the drying chamber 200. The fan 12 is located on the side of the condenser 400 away from the evaporator 100. The height of the second fin 410 of the condenser 400 along the second direction y is 60mm to 100mm, and the impeller diameter of the fan 12 is 100mm to 170mm.

[0098] Specifically, the height of the second fin 410 of the condenser 400 along the second direction y is the extension dimension Hf of the second fin 410 along the second direction y, which can be 60mm, 63mm, 65mm, 66mm, 68mm, 6mm, 70mm, 75mm, 77mm, 80mm, 85mm, 86mm, 90mm, 95mm, 99mm or 100mm, etc., and can be adjusted according to the usage requirements of the product; of course, other values ​​can also be used in other embodiments.

[0099] Specifically, the impeller diameter of the fan 12 can be 100mm, 103mm, 105mm, 108mm, 109mm, 115mm, 118mm, 120mm, 123mm, 125mm, 130mm, 135mm, 140mm, 142mm, 145mm, 148mm, 150mm, 152mm, 155mm, 160mm, 165mm, or 170mm, etc., which can be adjusted according to the product's usage requirements; of course, other values ​​can also be used in other embodiments.

[0100] In one application scenario, when the axis of the drum is parallel to the horizontal plane, and the axis of the drum is perpendicular to both the first direction x and the second direction y, and the evaporator 100 is located directly above the drum and the condenser 400 is located diagonally above the drum, it is easy to see that the second direction y is parallel to the direction of gravity. The height of the second fin 410 of the condenser 400 along the second direction y is the height of the second fin 410 of the condenser 400 along the direction of gravity.

[0101] This arrangement facilitates maximizing the overlap between the projections of the condenser 400 and the impeller of the fan 12 in the first direction x, thereby reducing the air resistance of the airflow from the condenser 400 to the fan 12 and increasing the airflow velocity.

[0102] In other embodiments, the height of the second fins of the condenser along the second direction can be adjusted according to the impeller diameter, or the size of the impeller diameter can be adjusted according to the height of the second fins of the condenser along the second direction.

[0103] In some embodiments, as shown in Figures 8 and 9, each first mounting area 130 is provided with a plurality of first mounting holes spaced apart along the second direction y for mounting a first refrigerant pipe 120; each second mounting area 430 is provided with a plurality of second mounting holes spaced apart along the second direction y for mounting a second refrigerant pipe 420. This arrangement facilitates the adjustment of the dimensions of the evaporator 100 or condenser 400 along the second direction y by adjusting the pipe spacing of the first refrigerant pipe 120 or the second refrigerant pipe 420 along the second direction y and the number of mounting holes in each mounting area.

[0104] In other embodiments, the second direction may intersect with or be opposite to the direction of gravity, and there is no specific limitation.

[0105] In some embodiments, the air volume of the fan 12 is 120m³. 3 / h. This configuration facilitates sufficient airflow for air exchange between the heat exchange chamber and the drying chamber 200, thereby improving the drying efficiency of the drying equipment 10.

[0106] In other embodiments, the airflow design of the fan can be adjusted according to the usage requirements of the product.

[0107] In some embodiments, referring to FIG8, the first mounting holes of two adjacent first mounting areas 130 are offset along the second direction y.

[0108] In some embodiments, referring to FIG9, the second mounting holes of two adjacent second mounting areas 430 are offset along the second direction y.

[0109] It should be noted that the misalignment setting refers to the projection misalignment of the mounting holes of two adjacent mounting areas in a direction perpendicular to the second direction y. In some embodiments, it can be set to be completely misaligned.

[0110] Since the mounting holes are used to install refrigerant pipes, and multiple mounting areas are arranged along the first direction x, when the mounting holes of two adjacent mounting areas 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 pipe in the mounting area near the windward side on the refrigerant pipe in another mounting area away from the windward side. Therefore, it can improve the overall heat exchange efficiency between the airflow and the condenser or evaporator.

[0111] In some embodiments, referring to Figures 2 and 7, the air duct housing 13 is disposed above the drum, and one or more of the evaporator 100, condenser 400, compressor, and fan 12 are connected to the air duct housing 13. The air duct housing 13 supports one or more of the evaporator 100, condenser 400, compressor, and fan 12 to improve the structural stability of the drying equipment 10, etc.

[0112] It should be noted that the specific connection method between it and the air duct housing 13 is not limited, such as fixed connection such as adhesive bonding or detachable connection.

[0113] In some embodiments, the duct housing 13 may have an installation position outside the heat exchange chamber for installing a compressor, fan 12, etc.

[0114] By integrating the compressor, fan 12, condenser 400, and evaporator 100 into the air duct housing 13, the structural layout can be optimized, the structural stability improved, and the structural volume reduced.

[0115] In some embodiments, the evaporator 100 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.

[0116] In some embodiments, the axis of the drum is perpendicular to both the first direction x and the second direction y (i.e., the third direction z is parallel to the axis of the drum), the axis of the drum is parallel to the horizontal plane, the second direction y is parallel to the direction of gravity, the drum and the evaporator 100 are arranged along the second direction y, and the evaporator 100 is located directly above the drum; the evaporator 100, the condenser 400 and the fan 12 are arranged sequentially along the first direction x (i.e., arranged along the horizontal direction), that is, the condenser 400 is located obliquely above the drum; along the first direction x, the area of ​​the second windward surface of the condenser 400 is greater than the area of ​​the first windward surface of the evaporator 100; wherein, the ratio of the area of ​​the second windward surface to the area of ​​the first windward surface is between 1.05 and 2; the condenser 400 includes a plurality of second fins 410 arranged at intervals along the third direction z, and the evaporator 100 includes a plurality of first fins 110 arranged at intervals along the third direction z.

[0117] Furthermore, the diameter of the drum ranges from 540mm to 570mm, the distance between the evaporator 100 and the condenser 400 along the first direction x ranges from 5mm to 35mm, the height difference between the bottom of the evaporator 100 and the bottom of the condenser 400 along the second direction y ranges from 3mm to 60mm, the height difference between the bottom of the evaporator 100 and the center point of the drum ranges from 270mm to 315mm, and the height difference between the bottom of the condenser 400 and the center point of the drum ranges from 210mm to 267mm.

[0118] Furthermore, the condenser 400 is located on the side of the fan 12 near the evaporator 100, and the height difference between the bottom of the condenser 400 and the center of the fan shaft 123 of the fan 12 ranges from -10mm to 30mm; the height of the second fin 410 of the condenser 400 along the second direction y ranges from 60mm to 100mm, and the impeller diameter of the fan 12 is from 100mm to 170mm; the first fin 110 of the evaporator 100 is provided with eight first mounting areas 130 arranged along the first direction x, and each first mounting area 130 includes a section along the second direction x. The condenser 400 has three first mounting holes arranged in a Y-shape. The first mounting holes in the first mounting area 130 are used to mount the first refrigerant pipe 120 of the evaporator 100. The outer diameter of the first refrigerant pipe 120 is 5mm. The second fins 410 of the condenser 400 have four second mounting areas 430 arranged in a first direction x. Each second mounting area 430 includes four second mounting holes arranged in a second direction y. The second mounting holes in the second mounting area 430 are used to mount the second refrigerant pipe 420 of the condenser 400. The outer diameter of the second refrigerant pipe 420 is 7mm. The fan 12 has an airflow of 120m³ / h. 3 / h.

[0119] Furthermore, the distance Fp between two adjacent first fins 110 along the third direction z is 1.5 mm, and the distance Fp between adjacent second fins 410 is 1.2 mm.

[0120] The above configuration makes it easier to ensure that the windward area of ​​the condenser 400 is larger than that of the evaporator 100, which can improve the overall heat exchange efficiency of the drying equipment 10 and thus save more energy.

[0121] In some embodiments (not shown), the height difference between the bottom of the condenser and the center point of the drum may decrease along a first direction. This arrangement allows the bottom of the condenser to fit as closely as possible to the drum wall, meaning the bottom of the condenser is not a flat surface; for example, it can be stepped or curved. This arrangement helps to maximize the heat exchange space of the condenser and improve its heat exchange efficiency.

[0122] In other embodiments, similar improvements can be made to the heat pump system with reference to the above embodiments, which will not be repeated here.

[0123] Unlike existing technologies, the area of ​​the second windward surface of the condenser in this application is larger than the area of ​​the first windward surface of the evaporator, and the ratio between the area of ​​the second windward surface and the area of ​​the first windward surface is less than or equal to 2. This facilitates increasing the heat exchange efficiency of the condenser by increasing its windward area, thereby improving the heat exchange efficiency of the heat pump system. Furthermore, increasing the windward area of ​​the condenser to increase its heat exchange efficiency facilitates optimizing the size of the condenser in the windward direction, which in turn facilitates optimizing the overall structural layout of the heat pump system. Moreover, increasing the windward area of ​​the condenser to increase its heat exchange efficiency reduces the risk of insufficient heat exchange due to an excessively large size of the condenser in the windward direction, thus improving the overall heat exchange efficiency.

[0124] This application further proposes a heat pump system 11, as shown in Figures 1 to 10. The heat pump system 11 includes a compressor, an evaporator 100, a condenser 400, and a throttling device. The evaporator 100 has a first air-facing surface; the condenser 400 has a second air-facing surface; the throttling device is disposed between the condenser 400 and the evaporator 100; the compressor, condenser 400, evaporator 100, and throttling device form a refrigerant circulation channel; wherein the area of ​​the second air-facing surface is larger than the area of ​​the first air-facing surface, and the ratio between the area of ​​the second air-facing surface and the area of ​​the first air-facing surface is less than or equal to 2.

[0125] Similar improvements can be made to the heat pump system 11 of this embodiment by referring to the above embodiments, and will not be described again.

[0126] 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.

[0127] 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 pump system, wherein, The heat pump system includes: compressor; The evaporator has a first air-facing surface; The condenser has a second air-facing surface, and the compressor, the condenser, and the evaporator form a refrigerant circulation channel; Wherein, the area of ​​the second windward surface is greater than the area of ​​the first windward surface, and the ratio between the area of ​​the second windward surface and the area of ​​the first windward surface is less than or equal to 2.

2. The heat pump system according to claim 1, wherein, The heat pump system also includes a throttling device, which is disposed between the condenser and the evaporator; The compressor, the condenser, the evaporator, and the throttling device form a refrigerant circulation channel.

3. The heat pump system according to claim 1 or 2, wherein, The ratio is greater than or equal to 1.

05.

4. The heat pump system according to claim 1 or 2, wherein, The direction from the first windward side to the leeward side of the evaporator is the first direction, and the projection of the evaporator toward the first direction is located within the projection of the condenser toward the first direction.

5. The heat pump system according to claim 4, wherein, The first fin of the evaporator is provided with a plurality of first mounting areas arranged along a first direction, and the first mounting areas are used to install the first refrigerant pipe of the evaporator; the second fin of the condenser is provided with a plurality of second mounting areas arranged along the first direction, and the second mounting areas are used to install the second refrigerant pipe of the condenser. Wherein, the outer diameter of the first refrigerant pipe is smaller than the outer diameter of the second refrigerant pipe, and the number of the first installation areas is greater than the number of the second installation areas.

6. The heat pump system according to claim 4, wherein, The dimension of the condenser along the first direction is smaller than the dimension of the evaporator along the first direction, and the spacing between the first fins of adjacent evaporators is greater than the spacing between the second fins of adjacent condensers.

7. A drying apparatus, wherein, 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 1 to 6, wherein at least the evaporator and the condenser are disposed in the heat exchange chamber.

8. The drying equipment according to claim 7, wherein, The drying chamber includes a drum, the axis of which is perpendicular to both a first direction and a second direction; the first direction is the direction from the first windward surface to the leeward surface of the evaporator, and the evaporator and the condenser are arranged along the first direction; the second direction is the arrangement direction of the evaporator and the drum.

9. The drying equipment according to claim 8, wherein, The drying chamber includes a drum. When the axis of the drum is parallel to the horizontal plane, the evaporator is located above the drum, and the perpendicular line from the condenser to the axis is set at an acute or obtuse angle with the direction of gravity of the drum.

10. The drying equipment according to claim 8, wherein, The axis of the drum is parallel to the horizontal plane. The side of the condenser away from the drum and the side of the evaporator away from the drum are located in the same horizontal plane. The height difference between the side of the condenser near the drum and the center point of the drum is less than the height difference between the side of the evaporator near the drum and the center point of the drum. The first direction is perpendicular to the second direction.

11. The drying equipment according to claim 8, wherein, The diameter of the drum is 540mm to 570mm, the distance between the evaporator and the condenser along the first direction is 5mm to 35mm, and the height difference between the side of the evaporator near the drum and the side of the condenser near the drum along the second direction is 3mm to 60mm. The first direction is perpendicular to the second direction.

12. The drying equipment according to claim 8, wherein, The diameter of the drum is 540mm to 570mm, the height difference between the side of the evaporator near the drum and the center point of the drum is 270mm to 315mm, and the height difference between the side of the condenser near the drum and the center point of the drum is 210mm to 267mm. The first direction is perpendicular to the second direction.

13. The drying equipment according to claim 10, wherein, The heat pump system also includes a fan, which is located at the air outlet of the air duct housing to guide the gas in the heat exchange chamber to the drying chamber. The fan is located on the side of the condenser away from the evaporator, and the height difference between the bottom of the condenser and the fan shaft is -10mm to 30mm.

14. The drying equipment according to claim 13, wherein, The heat pump system also includes a fan, which is located at the air outlet of the air duct housing to guide the gas in the heat exchange chamber to the drying chamber. The fan is located on the side of the condenser away from the evaporator. The height of the second fin of the condenser along the second direction is 60mm to 100mm, and the impeller diameter of the fan is 100mm to 170mm.

Images