Heat exchanger, heat pump system and drying equipment

Abstract

The utility model 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 drying chamber comprises a roller, the heat exchange cavity is used for being communicated with the roller, and the first direction is perpendicular to the axial direction of the roller. 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] The present application relates to the technical field of household appliances, in particular to a heat exchanger, a heat pump system and a drying device. BACKGROUND

[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 devices to achieve drying effects. In the prior art, the common heat pump system has low heat exchange efficiency, and the structure size of the drying device is large, and the structure needs to be optimized. CONTENT OF THE INVENTION

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

[0004] To solve the above technical problems, the present application provides a heat exchanger for a drying device, the heat exchanger is provided with a windward side and a leeward side, the direction from the windward side to the leeward side is a first direction, the drying device is provided with a drying chamber and a heat exchanger arranged along a second direction with the drying chamber, a heat exchange cavity where the heat exchanger is located is communicated with 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; wherein the first direction and the second direction are perpendicular; wherein the drying chamber includes a drum, the heat exchange cavity is used to communicate with the drum, and the first direction is perpendicular to the axial direction of the drum.

[0005] To solve the above technical problems, the present application further provides a heat pump system, the heat pump system includes a compressor, an evaporator and a condenser, the evaporator includes the above-mentioned heat exchanger; the compressor, the condenser and the evaporator form a refrigerant circulation channel; the evaporator and the condenser are arranged in the heat exchange cavity.

[0006] To solve the above technical problems, the present application further provides a drying device, the drying device includes a drying chamber, an air duct shell and the above-mentioned heat pump system, the air duct shell forms a heat exchange cavity communicated with the drying chamber; at least the evaporator and the condenser are arranged in the heat exchange cavity; wherein the evaporator and the condenser are arranged along the horizontal direction, and the second direction is the direction of gravity.

[0007] The application has the advantages that: the heat exchanger of the application is in communication with the drying chamber, which facilitates the circulation of airflow in the heat exchange cavity and the drying chamber, can facilitate heat exchange between the heat exchanger and the drying chamber, and can improve the drying efficiency of the drying chamber; the heat exchanger arranged in the heat exchange cavity can reduce the interference of the external environment on the heat exchanger, improve the working efficiency thereof, and reduce the probability of damage thereof; the arrangement of the heat exchanger and the drying chamber along the second direction can optimize the layout of the two, simplify the structure design, and improve the reliability of the work of the two, for example, when the second direction is the direction of gravity and the heat exchanger is arranged above the drying chamber, this arrangement facilitates the drying chamber to provide certain support for the heat exchanger, and improves the position 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 less than the second dimension thereof along the first direction, which facilitates the reduction of the overall size of the drying equipment in the second direction, and improves the structural compactness of the drying equipment; and the increase of the second dimension facilitates the increase of the total heat exchange area of the heat exchanger, and further improves the heat exchange efficiency of the heat pump system. BRIEF DESCRIPTION OF DRAWINGS

[0008] In order to more clearly illustrate the technical solutions in the embodiments of the application, the drawings needed in the embodiment description will be briefly introduced. Obviously, the drawings in the following description are only some embodiments of the application, and other drawings can be obtained by those skilled in the art without any creative effort. Among them:

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

[0010] Figure 2 is Figure 1 a cross-sectional structural schematic diagram of the embodiment;

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

[0012] Figure 4 is Figure 3 a side view schematic diagram of the embodiment;

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

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

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

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

[0017] Figure 9 is Figure 8 a side view schematic diagram of an embodiment of the present application;

[0018] Figure 10 is a structural schematic diagram of an embodiment of the heat exchanger of the present application. DETAILED DESCRIPTION

[0019] In the following description, for purposes of explanation and not limitation, specific details are set forth, such as a particular structure for a system, technique, or technology in order to provide a thorough understanding of the embodiments of the present application. However, it will be apparent to those skilled in the art that the present application can be practiced in other embodiments that depart from these specific details. In other instances, detailed descriptions of well-known systems, devices, circuits, and methods are omitted so as not to obscure the description of the present application with unnecessary detail.

[0020] The terms "first", "second", and the like in the present application are used to distinguish different objects, rather than to describe a particular order. In addition, the terms "include" and "have" and any variations thereof are intended to cover non-exclusive inclusion. It should be understood that when used in the specification and the appended claims, the term "include" indicates the presence of the described features, integers, steps, operations, elements, and / or components, but does not exclude one or more other features, integers, steps, operations, elements, components, and / or groups thereof. It should also be understood that the terms used in the present application specification are merely for the purpose of describing specific embodiments and are not intended to limit the present application. As used in the present application 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 be further understood that the term "and / or" as used in the present application specification is intended to refer to any combination of one or more of the associated listed items and all possible combinations thereof.

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

[0022] The technical solutions in the embodiments of the present application will be described clearly and completely in the following description of the drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, not all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor are within the scope of protection of the present application.

[0023] The present application first proposes a heat exchanger, as shown in Figures 1 to 10 Referring to Figures 1 to 5 The heat exchanger 100 is used in the drying apparatus 10, the heat exchanger 100 is provided with a windward side and a leeward side, a direction from the windward side to the leeward side is a first direction x, the drying apparatus 10 is provided with a drying chamber 200 and the heat exchanger 100 arranged along a second direction y with the drying chamber 200, a heat exchange cavity where the heat exchanger 100 is located is communicated with the drying chamber 200, a first dimension Hf of the heat exchanger 100 along the second direction y is less than a second dimension Tf along the first direction x; wherein the first direction x and the second direction y are arranged vertically; wherein the drying chamber 200 includes a drum, the heat exchange cavity is used for being communicated with the drum, and the first direction x is perpendicular to an axial direction of the drum.

[0024] It should be noted that the drying apparatus 10 of the present application can be, for example, a clothes dryer, a drying and washing integrated machine, a dryer, etc. at least having a drying function; the drying chamber 200 (i.e. the drum) is used for accommodating the to-be-dried objects, the drying chamber 200 of the present application can be used as a separate drying chamber 200, and can also be used as a drying and washing chamber, which is not limited in particular; the heat exchanger 100 is arranged along the second direction y with the drying chamber 200, which means that a projection of the heat exchanger 100 along a direction perpendicular to the second direction y is completely staggered and does not overlap with a projection of the drying chamber 200 along the direction; in the present application, the projection refers to the orthographic projection; the first direction x refers to the flow direction of the airflow flowing through the heat exchanger 100.

[0025] The heat exchange cavity where the heat exchanger 100 is located is communicated with the drying chamber 200, which facilitates the airflow to flow through the heat exchange cavity and the drying chamber 200, can facilitate the heat exchanger 100 and the drying chamber 200 to exchange heat, and can improve the drying efficiency of the drying chamber 200; the heat exchanger 100 is arranged in the heat exchange cavity, which can reduce the interference of the external environment on the heat exchanger 100, improve the working efficiency of the heat exchanger 100, and reduce the probability of damage to the heat exchanger 100; the heat exchanger 100 is arranged along the second direction y with the drying chamber 200, which can optimize the layout of the heat exchanger 100 and the drying chamber 200, simplify the structure design, and improve the working reliability of the heat exchanger 100 and the drying chamber 200; for example, when the second direction y is the direction of gravity and the heat exchanger 100 is arranged above the drying chamber 200, this arrangement facilitates the drying chamber 200 to provide certain support for the heat exchanger 100, and improves the position stability of the heat exchanger 100; since the heat exchanger 100 is arranged along the second direction y with the drying chamber 200, the first dimension Hf of the heat exchanger 100 along the second direction y is less than the second dimension Tf along the first direction x, which facilitates to reduce the overall size of the drying apparatus 10 in the second direction y, and improves the structural compactness of the drying apparatus 10; and it is convenient to increase the second dimension Tf to improve the total heat exchange area of the heat exchanger 100, and further improve the heat exchange efficiency of the heat pump system 11.

[0026] Further, the first direction x is perpendicular to the second direction y, facilitating the guiding of the airflow into the heat exchanger 100 and reducing the interference of the drying chamber 200 on the airflow guiding.

[0027] In some embodiments, referring to Figure 5 , the heat exchanger 100 comprises fins 110 and refrigerant pipes 120, the fins 110 are arranged to extend along the second direction y and the first direction x, and the refrigerant pipes 120 are arranged on the fins 110; wherein a first dimension Hf of the fins 110 along the second direction y is less than a second dimension Tf of the fins 110 along the first direction x.

[0028] It should be noted that the fins 110 extending along the second direction y and the first direction x means that the fins 110 extend in a plane perpendicular to the thickness direction of the fins 110 to form the main heat exchange surface thereof; the refrigerant pipes 120 circulate heat exchange medium for heat exchange; and the refrigerant pipes 120 are arranged on the fins 110, facilitating the use of the fins 110 to increase the heat exchange efficiency between the refrigerant pipes 120 and the airflow.

[0029] The fins 110 extending along the second direction y and the first direction x facilitate reducing the resistance of the airflow flowing through the heat exchanger 100 and facilitating the heat exchange between the main heat exchange surface of the fins 110 and the airflow; and the first dimension Hf of the fins 110 along the second direction y is less than the second dimension Tf of the fins 110 along the first direction x, facilitating the production convenience of the heat exchanger 100 with the first dimension Hf along the second direction y being less than the second dimension Tf along the first direction x.

[0030] In order 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 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., and is not limited in particular.

[0032] Such arrangement facilitates the heat exchanger 100 to achieve a smaller size in the second direction y, and the increase of the second dimension Tf in the first direction x can ensure the heat exchange performance of the heat exchanger 100, so that a higher heat exchange efficiency of the heat exchanger 100 can be achieved in a smaller height space (i.e. the first dimension Hf), thereby improving the overall drying efficiency of the drying equipment 10.

[0033] For example, in an application scenario, the heat exchanger 100 of the present embodiment is used as an evaporator, the inlet air temperature is 45℃, the inlet air humidity is 70%, and the inlet air volume is 100m 3 / h to 140m 3In the case of / h, when the ratio between the first dimension Hf and the second dimension Tf is 1.65, for example, the first dimension Hf is 84 cm and the second dimension is 50.8 cm, the heat exchange capacity 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, the first dimension Hf is 58.5 cm and the second dimension is 92.8 cm, the heat exchange capacity of the evaporator per unit time is 1909 W; the heat exchange efficiency of the improved evaporator can be improved by 11%.

[0034] In other embodiments, the ratio can also take other values according to the actual product structure needs to complete adaptive adjustment, for example, 0.45 or 0.96, etc., and the specific is not limited.

[0035] In some embodiments, referring to Figure 6 The heat exchanger 100 includes a plurality of fins 110 arranged at intervals along the third direction z, and the interval distance Fp between adjacent fins 110 is 1.4 mm to 2 mm; wherein the third direction z is arranged perpendicular to the second direction y and the first direction x.

[0036] It should be noted that the interval distance Fp between adjacent fins 110 refers to the interval distance Fp of adjacent fins 110 along the third direction z, which can be 1.4 mm, 1.43 mm, 1.45 mm, 1.46 mm, 1.5 mm, 1.51 mm, 1.55 mm, 1.57 mm, 1.6 mm, 1.66 mm, 1.7 mm, 1.72 mm, 1.78 mm, 1.8 mm, 1.85 mm, 1.9 mm, 1.92 mm, 1.95 mm, 1.98 or 2 mm, etc., and the specific is not limited.

[0037] The smaller the spacing distance Fp is, the greater the heat exchange amount of the heat exchanger per unit time is, that is, the higher the heat exchange efficiency is, but the air resistance of the heat exchanger 100 will also become greater, and when the spacing distance Fp is too small, for example, less than 1.3 mm, fluff and other foreign matters will be more likely to accumulate on the heat exchanger 100, affecting the heat exchange efficiency of the heat exchanger 100. Therefore, the third direction z is perpendicular to the first direction x, so that the spacing distance Fp formed between the adjacent fins 110 arranged at intervals along the third direction z can reduce the resistance encountered by the airflow flowing through the heat exchanger 100, so that the air resistance of the heat exchanger 100 as a whole is maintained at a relatively small level, and the spacing distance Fp is set to be in the range of 1.4 mm to 2 mm, which can reduce the overall size of the heat exchanger 100 under the premise of ensuring a relatively small air resistance of the heat exchanger 100, ensure the heat exchange efficiency of the heat exchanger 100, improve the applicability of the heat exchanger 100, and reduce the risk of fluff and other foreign matters accumulating on the heat exchanger 100. For example, when the second dimension Tf of the heat exchanger 100 along the first direction x is relatively large (for example, the ratio between the first dimension Hf and the second dimension Tf is 0.5 to 0.95), the spacing distance Fp is set to be in the range of 1.4 mm to 2 mm, which can effectively reduce the air resistance of the heat exchanger 100, and can enable the heat exchanger 100 to achieve efficient heat exchange even when the second dimension Tf along the first direction x is relatively large.

[0038] In other embodiments, based on different requirements for parameters such as heat exchange efficiency of the heat exchanger, the spacing distance between the adjacent fins can also be other values, for example, 1.35 mm or 2.1 mm, etc., and the specific value is not limited.

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

[0040] In an application scenario, when the inlet air temperature of the heat exchanger 100 is 45℃, the inlet air humidity is 70%, and the inlet air volume is 100m 3 / h to 140m 3 / h, as the spacing distance Fp between the adjacent fins 110 increases, the heat exchange amount of the heat exchanger decreases, and when the spacing distance Fp is greater than 1.6 mm, as the Fp increases, the attenuation amplitude of the heat exchange amount increases obviously, that is, the influence of the increase of the spacing distance Fp on the heat exchange amount attenuation becomes greater and greater; as the spacing distance Fp between the adjacent fins 110 increases, the air resistance of the heat exchanger also decreases, and when the spacing distance Fp increases to greater than 1.6 mm, the reduction amplitude of the air resistance becomes obviously smaller, that is, the contribution of the increase of the spacing distance Fp to the reduction of the air resistance becomes smaller and smaller. Based on this, in order to enable the heat exchanger 100 to obtain smaller air resistance and greater heat exchange amount, the spacing distance Fp is preferably 1.5 mm.

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

[0042] The spacing distance Fp between the adjacent fins 110 spaced along the third direction z is set to 1.5 mm, which can effectively maintain the air resistance of the heat exchanger 100 at a small level, and can enable the heat exchanger 100 to achieve high-efficiency heat exchange even in the case that the second dimension Tf in the first direction x is large.

[0043] In some embodiments, referring to Figure 5 、 Figure 6 、 Figure 7 The fin 110 is provided with a plurality of mounting areas 300 arranged along the first direction x, and each mounting area 300 is provided with a plurality of mounting holes spaced along the second direction y, which are used for mounting the refrigerant pipe 120.

[0044] It should be noted that each mounting area 300 includes a plurality of sub-mounting areas of the same size arranged in sequence along the second direction y, wherein the plurality of mounting holes are respectively located in the corresponding sub-mounting areas, and the positions of the plurality of mounting holes in the corresponding sub-mounting areas are the same. Therefore, the pipe spacing a of the refrigerant pipe 120 along the second direction y is the spacing between two adjacent mounting holes along the second direction y, and the spacing between two adjacent mounting holes along the second direction y is equal to the size of the sub-mounting area along the second direction y. Therefore, the size of the mounting area 300 along the second direction y is equal to the size of the sub-mounting area along the second direction y multiplied by the number of sub-mounting areas along the second direction y.

[0045] The above arrangement facilitates 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; and facilitates 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 arranged along the first direction x of the fin 110.

[0046] In some embodiments, the specific number and arrangement of the refrigerant pipe 120 are not limited.

[0047] For example, the heat exchanger 100 includes one solderless serpentine disc-shaped bent pipe, which is used as the refrigerant pipe 120, i.e., the refrigerant pipe 120 is serpentine disc-shaped and passes through all the mounting holes on the fin 110 to be arranged on the fin 110; for another example, the heat exchanger 100 includes a plurality of serpentine disc-shaped bent pipes, each of which passes through different mounting holes on the fin 110, and the plurality of serpentine disc-shaped bent pipes are used as a plurality of refrigerant pipes 120; specifically, the serpentine disc-shaped bent pipe is not limited in the disc winding sequence, i.e., the serpentine disc-shaped bent pipe is not limited in the sequence of passing through the plurality of mounting holes, which can be adjusted according to the production process or actual product demand.

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

[0049] It should be noted that the staggered arrangement refers to the projections of the mounting holes of two adjacent mounting regions 300 in a direction perpendicular to the second direction y are arranged staggered, which in some embodiments can be arranged completely staggered.

[0050] Since the mounting holes are used for mounting the refrigerant pipes 120, and the plurality of mounting regions 300 are arranged along the first direction x, when the mounting holes of two adjacent mounting regions 300 are arranged staggered along the second direction y perpendicular to the first direction x, the shielding effect of the refrigerant pipes 120 in the mounting region 300 close to the windward side on the refrigerant pipes 120 in the other mounting region 300 far from the windward side can be reduced, and the overall heat exchange efficiency of the airflow and the refrigerant pipes 120 of the heat exchanger 100 can be improved.

[0051] In some embodiments, referring to Figure 5 , Figure 6 , Figure 7 , the fin 110 is provided with 8 mounting regions 300 arranged along the first direction x, each mounting region 300 is provided with 3 mounting holes arranged spaced apart along the second direction y, and the mounting holes are used for mounting the refrigerant pipes 120; wherein the outer diameter of the refrigerant pipe 120 is 5 mm, the pipe spacing a of the refrigerant pipe 120 along the second direction y is 19.5 mm; and the size of the mounting region 300 along the first direction x is 11.6 mm.

[0052] In this embodiment, each mounting region 300 includes 3 sub-mounting regions of the same size arranged in sequence along the second direction y, wherein the 3 mounting holes are respectively located in the corresponding sub-mounting regions, and the positions of the 3 mounting holes in the corresponding sub-mounting regions are the same, so the pipe spacing a of the refrigerant pipe 120 along the second direction y is equal to the spacing between two adjacent mounting holes along the second direction y, and the spacing between two adjacent mounting holes along the second direction y is equal to the size of the sub-mounting region along the second direction y, so the size of the mounting region 300 along the second direction y is equal to the size of the sub-mounting region along the second direction y multiplied by 3.

[0053] In an application scenario, when the overall height of the drying equipment is in the range of 895 mm to 850 mm, the inlet air temperature of the heat exchanger is 45℃, the inlet air humidity is 70%, and the air volume is 100 m 3 / h-140m 3 / h, the temperature in the refrigerant pipe 120 is -6℃ to 35℃, and the number of mounting holes of each mounting area 300 is 3, as the number of mounting areas increases, both the heat exchange capacity of the heat exchanger and the air resistance increase. When the number of mounting areas increases to 8, the increasing rate of the heat exchange capacity begins to decrease obviously, therefore, it is preferred to determine the number of mounting areas as 8, which can provide sufficient heat exchanger area in a compact space to realize the fast drying function, and under this setting, the fan can overcome the corresponding air resistance to realize normal work.

[0054] In addition, the outer diameter of the refrigerant pipe 120 can be set as 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 size of the mounting area 300 along the first direction x is 11.6mm.

[0055] In other embodiments, the inlet air temperature can be further set to be 5℃ to 50℃, the inlet air humidity can be further set to be 20% to 100%, and the air volume can be further set to be 65m 3 / h to 220m 3 / h.

[0056] In another application scenario, when the inlet air temperature of the heat exchanger is 45℃, the inlet air humidity is 70%, and the air volume is 100m 3 / h-140m 3 / h, the temperature in the refrigerant pipe 120 is -6℃ to 35℃, and the number of mounting holes of each mounting area 300 is 3, as the number of mounting areas increases, both the heat exchange capacity of the heat exchanger and the air resistance increase. When the number of mounting areas increases to 8, the increasing rate of the heat exchange capacity begins to decrease obviously, therefore, it is preferred to determine the number of mounting areas as 8, which can provide sufficient heat exchanger area in a compact space to realize the fast drying function, and under this setting, the fan can overcome the corresponding air resistance to realize normal work.

[0057] In other embodiments, the inlet air temperature can be further set to be 5℃ to 50℃, the inlet air humidity can be further set to be 20% to 100%, and the air volume can be further set to be 65m 3 / h to 220m 3 / h.

[0058] The beneficial effect of the above arrangement is that the tube spacing a of the refrigerant pipe 120 along the second direction y is 19.5 mm, and three mounting holes for mounting the refrigerant pipe 120 are arranged at intervals along the second direction y in each mounting area 300, so that it is convenient to arrange the size of the mounting area 300 along the second direction y as 58.5 mm, and thus it is convenient to arrange the first size Hf of the heat exchanger 100 along the second direction y as 58.5 mm; the size of the mounting area 300 along the first direction x for mounting the refrigerant pipe 120 is 11.6 mm, and the fin 110 is provided with eight mounting areas 300 arranged along the first direction x, so that it is convenient to arrange the size of the fin 110 along the first direction x as 92.8 mm, and thus it is convenient to arrange the second size Tf of the heat exchanger 100 along the first direction x as 92.8 mm; and thus the first size Hf is 58.5 mm and the second size Tf is 92.8 mm, which is more convenient to realize that the ratio of the first size Hf to the second size Tf is close to 0.63. This arrangement is convenient to sufficiently reduce the overall height of the heat exchanger 100, so that the design of the entire drying apparatus 10 is more compact.

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

[0060] Referring to Figure 7 , the fin 110 is provided with eight mounting areas 300 arranged along the first direction x, and each mounting area 300 is provided with a first mounting hole, a second mounting hole and a third mounting hole arranged at intervals along the second direction y, so that there are eight first mounting holes, eight second mounting holes and eight third mounting holes on the fin 110; the heat exchanger 100 includes a first heat exchange pipe 121, a second heat exchange pipe 122 and a third heat exchange pipe 123 in the shape of a serpentine disc, the first heat exchange pipe 121, the second heat exchange pipe 122 and the third heat exchange pipe 123 serve as the refrigerant pipe 120, the first heat exchange pipe 121 is mounted in the first mounting hole, the second heat exchange pipe 122 is mounted in the second mounting hole, and the third heat exchange pipe 123 is mounted in the third mounting hole; wherein the first heat exchange pipe 121, the second heat exchange pipe 122 and the third heat exchange pipe 123 are arranged at intervals along the second direction y, and adjacent two first mounting holes are arranged at intervals along the second direction y.

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

[0062] In other embodiments, referring to Figure 8 , Figure 9 , Figure 10The fin 110 is provided with 6 mounting areas 300 arranged along the first direction x, and each mounting area 300 is provided with 4 mounting holes arranged along the second direction y, which are used for mounting the refrigerant pipe 120; wherein the outer diameter of the refrigerant pipe 120 is 5 mm, the pipe spacing a of the refrigerant pipe 120 along the second direction y is 14.5 mm; and the size of the mounting area 300 along the first direction x is 12.56 mm.

[0063] In an application scenario, when the overall height of the drying equipment is in the range of 895 mm to 850 mm, the inlet air temperature of the heat exchanger is 45℃, the inlet air humidity is 70%, the air volume is 100 m 3 / h-140 m 3 / h, and the temperature in the refrigerant pipe 120 is -6℃ to 35℃, and the number of mounting holes of each mounting area 300 is 4, as the number of mounting areas increases, the heat exchange capacity and the air resistance of the heat exchanger both increase. When the number of mounting areas increases to 6, the increase rate of the heat exchange capacity begins to decrease obviously, therefore, it is preferred to determine the number of mounting areas as 6, which can provide sufficient heat exchanger area in a compact space to realize the fast drying function, and under this setting, the air wheel can overcome the corresponding air resistance to realize normal work.

[0064] In other embodiments, the outer diameter of the refrigerant pipe 120 can be further set as 5 mm, the pipe spacing of the refrigerant pipe 120 along the second direction y is 14.5 mm, and the size of the mounting area 300 along the first direction x is 12.56 mm.

[0065] In other embodiments, the inlet air temperature can be further set in the range of 5℃ to 50℃, the inlet air humidity can be further set in the range of 20% to 100%, and the air volume can be further set in the range of 65 m 3 / h to 220 m 3 / h.

[0066] In another application scenario, when the inlet air temperature of the heat exchanger is 45℃, the inlet air humidity is 70%, the air volume is 100 m 3 / h-140 m 3 / h, and the temperature in the refrigerant pipe 120 is -6℃ to 35℃, and the number of mounting areas 300 is 6, as the number of mounting holes in the mounting area increases, the heat exchange capacity of the heat exchanger increases, and the air resistance decreases. When the number of mounting areas increases to 4, the increase rate of the heat exchange capacity begins to decrease obviously, and the decrease rate of the air resistance also decreases, therefore, it is preferred to determine the number of mounting holes as 4, which can increase the heat exchange capacity of the heat exchanger 100 as much as possible and reduce the air resistance of the heat exchanger 100.

[0067] In other embodiments, the inlet air temperature can be further set in the range of 5℃ to 50℃, the inlet air humidity can be further set in the range of 20% to 100%, and the air volume can be further set in the range of 65 m 3 / h to 220 m3 / h.

[0068] The beneficial effects of the above arrangement are that the tube pitch of the refrigerant pipe 120 along the second direction y is 14.5 mm, 4 mounting holes for mounting the refrigerant pipe 120 are arranged at intervals along the second direction y for each mounting area 300, so it is convenient to arrange the size of the mounting area 300 along the second direction y as 58 mm, and thus it is convenient to arrange the first size Hf of the heat exchanger 100 along the second direction y as 58 mm; the size of the mounting area 300 along the first direction x for mounting the refrigerant pipe 120 is 12.56 mm, and the fin 110 is provided with 6 mounting areas 300 arranged along the first direction x, so it is convenient to arrange the size of the fin 110 along the first direction x as 75.36 mm, and thus it is convenient to arrange the second size Tf of the heat exchanger 100 along the first direction x as 75.36 mm; and thus the first size Hf is 58 mm and the second size Tf is 75.36 mm, which is more convenient to realize that the ratio of the first size Hf to the second size Tf is close to 0.77. This arrangement is convenient to sufficiently reduce the overall height of the heat exchanger 100, so that the design of the entire drying equipment 10 is more compact.

[0069] In other embodiments, the fin can also be provided with other numbers of mounting areas (such as 4, 2 or 1, etc.) arranged along the first direction; further, the number of mounting holes arranged at intervals along the second direction for each mounting area can also be adjusted according to actual product needs (such as 2 mounting holes for each mounting area, etc.); and different mounting areas can also be provided with different numbers of mounting holes, which are not limited in particular.

[0070] In other embodiments, the outer diameter of the refrigerant pipe can also be set as other values according to actual product needs, which are not limited in particular.

[0071] In other embodiments, the tube pitch of the refrigerant pipe along the second direction and the size of the mounting area along the first direction can also be set as other values according to actual product needs, which are not limited in particular.

[0072] In other embodiments, similar improvements can also be made for the heat exchanger, which are not described here again.

[0073] The application further proposes a heat pump system 11, which comprises a compressor, an evaporator 600, and a condenser 400, the evaporator 600 comprising a heat exchanger 100; the compressor, the condenser 400 and the evaporator 600 form a refrigerant circulation channel; and the evaporator 600 and the condenser 400 are arranged in a heat exchange cavity.

[0074] The specific embodiments and working principles of the heat exchanger 100 can be referred to the above embodiments, which are not described here again.

[0075] The refrigerant circulating channel circulates the refrigerant, and the refrigerant exchanges heat with the outside airflow through the refrigerant pipe and the fins.

[0076] The heat pump system 11 of the present application can be used in the drying device 10, which is provided with a drying chamber 200. The evaporator 600 of the heat pump system 11 is arranged along the second direction y with the drying chamber 200, and the heat exchange cavity where the evaporator 600 is located is in communication with the drying chamber 200. The evaporator 600 and the condenser 400 are located in the heat exchange cavity in communication with 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 the second dimension Tf of the evaporator 600 along the first direction x, and the first direction x is arranged perpendicularly to the second direction y. The condenser 400 and the 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 the refrigerant through the compressor, the condenser 400 and the evaporator 600.

[0077] In an application scenario, the airflow first flows through the evaporator 600 and then flows 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, the humid airflow condenses water droplets on the surface of the evaporator 600, exchanges heat with the evaporator 600, and is converted into dry airflow. The dry airflow absorbs heat when flowing through the condenser 400, and becomes high-temperature dry airflow. The high-temperature dry airflow flows into the drying chamber 200, so as to heat and dry the objects to be dried in the drying process. The circulation of the airflow between the heat exchange cavity and the drying chamber 200 and the circulation of the refrigerant in the heat exchange cavity can realize the drying of the objects to be dried in the drying chamber 200.

[0078] The heat pump system 11 further comprises a throttling device arranged between the condenser 400 and the evaporator 600. The compressor is the power source of the heat pump system 11, which is used to change the low-temperature and low-pressure refrigerant vapor from the evaporator 600 into high-temperature and high-pressure refrigerant vapor through adiabatic compression, and supply the high-temperature and high-pressure refrigerant vapor to the condenser 400. The condenser 400 condenses the high-temperature and high-pressure refrigerant vapor from the compressor under the condition of constant pressure, and radiates heat to the heat exchange cavity, i.e. exchanges heat with the airflow in the heat exchange cavity. The refrigerant in the condenser 400 becomes high-pressure supercooled liquid. The high-pressure supercooled liquid from the condenser 400 becomes low-temperature and low-pressure refrigerant vapor after throttling by the throttling device, and enters the evaporator 600 to evaporate. The low-temperature and low-pressure refrigerant vapor after throttling boils in the evaporator 600 under the condition of constant pressure, absorbs the heat of the wet heat medium (for example, the humid airflow entering the heat exchange cavity) in the heat exchange cavity, and becomes low-temperature and low-pressure refrigerant vapor to the compressor. At the same time, the water vapor in the wet heat medium in the heat exchange cavity is condensed into condensed water and discharged.

[0079] The heat pump system 11 of this embodiment includes an evaporator 600, and the evaporator 600 includes the above-mentioned 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, which is convenient for reducing the overall size of the drying equipment 10 in the second direction y, and convenient for 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 setting 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 connected to the heat exchange chamber. The humid air flow 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 flow flowing out of the condenser 400 flows into the drying chamber 200 from the heat exchange chamber 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 the condenser 400 in the first direction x to reduce the wind resistance of the airflow flowing through the evaporator 600 into the condenser 400, the first direction x is set perpendicular to the second direction y, which can facilitate the arrangement of the evaporator 600 and the condenser 400 in the horizontal direction, and not only facilitates the optimization of the layout of the two, but also facilitates the arrangement of the condenser 400 above the drying chamber 200, which can simplify the structural design of the heat exchange cavity and the refrigerant flow channel where the two are located, save costs and improve the reliability of their operation.

[0083] In other embodiments, the second direction may also intersect with or be opposite to the direction of gravity, which is not specifically limited.

[0084] In some embodiments, see Figure 4 、 Figure 9 The refrigerant pipe 120 of the heat exchanger is provided with an inlet and an outlet, and the evaporator 600 is provided with a plurality of 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, and the condenser 400 is provided with a second refrigerant pipe 1202. The inlets of multiple first refrigerant pipes 1201 are connected to the outlet of the same second refrigerant pipe 1202, and the inlets of multiple second refrigerant pipes 1202 are connected to the outlet of the compressor.

[0085] In a complete process of dehumidifying and heating the air flow, the heat exchange amount of the condenser 400 is usually greater than that of the evaporator 600 because the condenser 400 needs to heat the dry air flow to become a high-temperature dry air flow. Therefore, the outer diameter of the second refrigerant pipe 1202 (the refrigerant pipe 120 of the condenser 400) is usually greater than that of the first refrigerant pipe 1201 (the refrigerant pipe 120 of the evaporator 600). Since the evaporator 600, the condenser 400, and the compressor form a refrigerant circulation channel, the evaporator 600 is provided with a plurality of first refrigerant pipes 1201, so that the refrigerant flowing out of the second refrigerant pipe 1202 with a larger outer diameter can be branched when entering the first refrigerant pipe 1201 with a smaller outer diameter, thereby reducing the influence of the smaller outer diameter of the first refrigerant pipe 1201 on the flow rate of the refrigerant. Therefore, the flow rate of the refrigerant in the heat pump system 11 as a whole can be improved, and the overall heat exchange effect can be improved.

[0086] In some embodiments, referring to Figure 4 , the plurality of first refrigerant pipes 1201 are arranged at intervals along the second direction y.

[0087] This arrangement facilitates production and assembly, improves the simplicity of the structural design, and facilitates the formation of gaps between the plurality of first refrigerant pipes 1201 along the second direction y, thereby facilitating the flow of air and improving the heat exchange efficiency.

[0088] In other embodiments, the plurality of first refrigerant pipes can also be arranged in a cross pattern without limitation on the winding manner.

[0089] In an application scenario, the heat exchanger 100 is used as an evaporator. Referring to Figure 9 , the plurality of first refrigerant pipes 1201 are arranged in a cross pattern. The refrigerant enters the evaporator and is branched into two paths to flow into two first refrigerant pipes 1201. The flow in the two first refrigerant pipes 1201 is usually unevenly distributed. The refrigerant in the first refrigerant pipe 1201 with a larger flow rate is excessive, so that the refrigerant has not been completely evaporated when leaving the evaporator, resulting in flow waste. The flow of the refrigerant in the other first refrigerant pipe 1201 is too small, so that the refrigerant is completely evaporated in the flow path, resulting in waste of evaporation area. At this time, the plurality of first refrigerant pipes 1201 arranged in a cross pattern can make the refrigerant in the first refrigerant pipe 1201 with a larger flow rate flow to the side of the first refrigerant pipe 1201 with a smaller flow rate to realize heat exchange, thereby making the overall heat exchange effect of the evaporator more uniform.

[0090] The application further provides a drying apparatus 10, which comprises a drying chamber 200, an air duct shell, a heat pump system 11, the air duct shell is formed with a heat exchange cavity in communication with the drying chamber 200; the heat pump system 11 comprises a compressor, an evaporator 600 and a condenser 400, at least the evaporator 600 and the condenser 400 are arranged in the heat exchange cavity; the evaporator 600 and the condenser 400 are arranged in a horizontal direction, and the second direction y is the direction of gravity.

[0091] The specific embodiments and working principles of the heat pump system 11 can refer to the above embodiments, and will not be described herein again; the specific embodiments and working principles of the heat exchange device 100 can refer to the above embodiments, and will not be described herein again.

[0092] It should be noted that the drying apparatus 10 of the application can be, for example, a clothes dryer, a dry cleaning all-in-one machine, a dryer or the like at least having a drying function; the drying chamber 200 is used for accommodating articles 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 staggered in the horizontal direction, i.e., the projection of the evaporator 600 along a direction perpendicular to the horizontal direction is completely staggered with and does not overlap with the projection of the condenser 400 along the direction.

[0093] The heat exchange cavity is in communication with the drying chamber 200, and the evaporator 600 and the condenser 400 are arranged in the heat exchange cavity, so that the evaporator 600 and the condenser 400 can exchange heat with the drying chamber 200, improve the drying efficiency of the drying chamber 200, and reduce the interference of the external environment on the evaporator 600 and the condenser 400, improve the working efficiency and reduce the probability of damage; the evaporator 600 and the condenser 400 are arranged in a horizontal direction, which can optimize the layout of the two, simplify the structural design of the heat exchange cavity and the refrigerant flow channel where the two are arranged, save costs and improve the reliability of the working of the two; the heat exchange device 100 and the drying chamber 200 are arranged in the direction of gravity (i.e., the second direction y), which can optimize the layout of the two; when the heat exchange device 100 is arranged above the drying chamber 200, this arrangement facilitates the drying chamber 200 to provide certain support for the heat exchange device 100, and improves the position stability of the heat exchange device 100; the drying apparatus 10 of the embodiment comprises the above-described evaporator 600, and the evaporator 600 comprises the above-described heat exchange device 100; since the evaporator 600 is arranged in the second direction y, the first dimension Hf of the evaporator 600 in the second direction y is less than the second dimension Tf of the evaporator 600 in the first direction x, which facilitates the reduction of the overall size of the drying apparatus 10 in the second direction y, and facilitates the increase of the second dimension Tf to improve the total heat exchange area of the evaporator 600, and further improve the drying efficiency of the drying apparatus 10, so that this arrangement can improve the structural compactness and the drying efficiency of the drying apparatus 10.

[0094] In some embodiments, the evaporator 600 is arranged close to the air inlet of the heat exchange cavity, and the condenser 400 is arranged close to the air outlet of the heat exchange cavity. The air inlet of the heat exchange cavity is in communication with the air outlet of the drying chamber 200, which can optimize the structure of the entire drying device 10.

[0095] In some embodiments, the drying device 10 further comprises a fan 12. The fan 12 sucks the humid air flow in the drying chamber 200 into the heat exchange cavity, which facilitates the circulation of the air flow between the drying chamber 200 and the heat exchange cavity.

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

[0097] It should be noted that the specific connection mode of the air duct housing is not limited, such as fixed connection or detachable connection, etc.

[0098] In some embodiments, the air duct housing can be provided with a mounting position outside the heat exchange cavity, which is used to mount the compressor, the fan, etc.

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

[0100] In some embodiments, the drying chamber 200 comprises a drum. The air duct housing is arranged above the drum. The evaporator 600 and the condenser 400 are arranged in the heat exchange cavity formed by the air duct housing in sequence along the first direction x.

[0101] In some embodiments, the axial direction of the drum is perpendicular to the first direction x and the second direction y, i.e., the third direction z is parallel to the axial direction of the drum. The second direction y is the direction of gravity. The drum and the evaporator 600 are arranged along the second direction y. The evaporator 600 is arranged above the drum. The evaporator 600 and the condenser 400 are arranged in sequence along the first direction x.

[0102] The evaporator 600 and the condenser 400 are arranged along the first direction x, so that the air flow passing through the evaporator 600 can smoothly enter the condenser 400, reducing the flow resistance of the air flow, improving the overall heat exchange efficiency of the heat pump system 11, and optimizing the structural arrangement, reducing the size, and facilitating the positioning of the fan 12 and the optimization of the air duct structure. Further, when the evaporator 600 and the condenser 400 are arranged along the first direction x, the first direction x is perpendicular to the axial direction of the drum, which can facilitate the full use of the space above the drum to arrange the evaporator 600 and the condenser 400. For example, the condenser 400 with larger heat exchange capacity can be arranged in the larger space above the drum, thereby facilitating the compactness of the drying apparatus 10 and realizing miniaturization. In other embodiments, the evaporator 600 and the condenser can also be arranged along other directions, and the air flow can first pass through the evaporator 600 for dehumidification and then flow into the condenser for heating, without limitation.

[0103] In some embodiments, the condenser 400 is arranged above the drum, and the top of the condenser 400 is flush with the top of the evaporator 600. This arrangement facilitates the maximization of the heat exchange space of the condenser 400 and the improvement of the heat exchange efficiency of the condenser 400, and this arrangement facilitates the reliability of the overall structure of the drying apparatus 10.

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

[0105] This arrangement facilitates the condenser 400 to be as close as possible to the drum wall, i.e., the bottom of the condenser 400 is not a flat surface, for example, it can be arranged in a stepped shape (see Figure 8 ) or an arc shape, which facilitates the maximization of the heat exchange space of the condenser 400 and the improvement of the heat exchange efficiency of the condenser 400.

[0106] In other embodiments, the first direction can also be arranged parallel to the axial direction of the drum and perpendicular to the second direction, without limitation.

[0107] In some embodiments, the drying apparatus 10 further comprises a partition plate arranged on the bottom wall of the heat exchange cavity to form a water collecting groove on the bottom wall. The water collecting groove is used to collect liquid flowing from the evaporator 600, such as condensate water generated by the evaporator 600.

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

[0109] Compared with the prior art, the heat exchanger of the application is communicated with the drying chamber through the heat exchange cavity, which facilitates the circulation of airflow in the heat exchange cavity and the drying chamber, can facilitate heat exchange between the heat exchanger and the drying chamber, and can improve the drying efficiency of the drying chamber; the heat exchanger arranged in the heat exchange cavity can reduce the interference of the external environment on the heat exchanger, improve the working efficiency thereof, and reduce the probability of damage thereof; the heat exchanger and the drying chamber are arranged along the second direction, which can optimize the layout of the heat exchanger and the drying chamber, simplify the structure design, and improve the reliability of the heat exchanger and the drying chamber; for example, when the second direction is the direction of gravity and the heat exchanger is arranged above the drying chamber, this arrangement facilitates the drying chamber to provide certain support for the heat exchanger, thereby improving the position 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 less than the second dimension of the heat exchanger along the first direction, which facilitates the reduction of the overall size of the drying equipment in the second direction and improves the compactness of the drying equipment; and the increase of the second dimension facilitates the increase of 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 drawings herein are only used to show the structural relationship and connection relationship of the product of the application, and do not limit the specific structural size of the product of the application.

[0111] The above is only an embodiment of the application, and does not limit the patent scope of the application, and any equivalent structure or equivalent process transformation using the content of the specification and drawings, or direct or indirect application in other related technical fields, are also included in the patent protection scope of the application.

Claims

1. A heat exchanger, characterized in that: For use in 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 includes a drying chamber and the heat exchanger arranged along a second direction with the drying chamber, a heat exchange cavity where the heat exchanger is located is connected to the drying chamber, and a first dimension of the heat exchanger along the second direction is smaller than a second dimension along the first direction; Wherein, the first direction is arranged perpendicular to the second direction; Wherein, the drying chamber includes a drum, the heat exchange cavity is used to communicate with the drum, and the first direction is perpendicular to the axial direction of the drum.

2. The heat exchanger according to claim 1, characterized in that The heat exchanger comprises: Fins are extended along the first direction and the second direction; a refrigerant pipe, disposed on the fin; Wherein, a first dimension of the fin along the second direction is smaller than a second dimension of the fin along the first direction.

3. The heat exchanger according to claim 1 or 2, characterized in that: A ratio between the first size and the second size 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, and a spacing distance between adjacent fins is 1.4 mm to 2 mm; Wherein, the third direction is perpendicular to the first direction and the second direction respectively.

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

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

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

8. A heat pump system, characterized in that: The heat pump system comprises: compressor; An evaporator, the evaporator comprising the heat exchanger according to any one of claims 1 to 7; Condenser, the compressor, the condenser and the evaporator form a refrigerant circulation channel; The evaporator and the condenser are used to be arranged in the heat exchange cavity.

9. The heat pump system according to claim 8, characterized in that The refrigerant pipe of the heat exchanger is provided with an inlet and an outlet, the evaporator is provided with multiple first refrigerant pipes, and the condenser is provided with a second refrigerant pipe. 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 comprises: drying room; an air duct housing, wherein the air duct housing is formed with a heat exchange cavity communicating 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 arranged in the heat exchange chamber; in, The evaporator and the condenser are arranged in a horizontal direction, and the second direction is a gravity direction.

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