Clothes dryer

Abstract

The embodiment of the utility model belongs to the clothes processing technology, and provides a clothes dryer. The clothes dryer comprises a shell, an air guide plate and an air impeller. The air guide plate is installed outside the shell, a volute is arranged in the air guide plate, and the volute is communicated with the interior of the barrel. At least part of the fan impeller is arranged in the volute, and the fan impeller is constructed to be connected with the motor and driven by the motor to rotate to generate airflow. The volute is constructed to be capable of guiding airflow generated by the fan blade wheel into the barrel so as to dry the to-be-dried objects in the barrel. The outer diameter of the wind impeller is larger than or equal to 130 mm and smaller than or equal to 140 mm, and the inner diameter of the wind impeller is larger than or equal to 100 mm and smaller than or equal to 110 mm. According to the clothes dryer, the drying speed is not affected, meanwhile, the wind noise can be greatly reduced, the power consumption of the whole clothes dryer is reduced, the energy efficiency is improved, the drying speed, the power consumption and the wind noise of the clothes dryer can be well balanced, and the clothes dryer is more power-saving.

Description

[0001] This application claims the priority of a Chinese patent application with the application number 202421590645.0, titled "Clothes Dryer", filed with the Chinese Patent Office on July 5, 2024, the entire content of which is incorporated herein by reference. Technical Field

[0002] Embodiments of the present application relate to clothing treatment technologies. In particular, it relates to a clothes dryer. Background Art

[0003] A clothes dryer is a type of household cleaning appliance that uses electric heating to instantly evaporate and dry the moisture in washed clothes.

[0004] With the progress of technology, people have put forward higher requirements for the energy efficiency, power, etc. of clothes dryers. The internal circulation of air flow in the clothes dryer is a basic condition for drying clothes. The power source of the internal circulation of air flow in the clothes dryer comes from the wind impeller. The size parameters of the wind impeller determine the circulation speed of the internal air, which in turn affects the drying speed. The outer diameter of the existing wind impeller is relatively large. Although it can generate a relatively large air flow rate and improve the drying speed, at the same time, it will increase the power and power consumption of the clothes dryer, and the wind impeller will generate a relatively large wind noise when rotating, making the overall experience of the clothes dryer not very friendly.

[0005] Therefore, it is necessary to balance the drying speed, power consumption, and wind noise of the clothes dryer. And how to balance the drying speed, power consumption, and wind noise of the clothes dryer has become a technical problem to be solved. Utility Model Content

[0006] The purpose of the present application is to solve at least the above problems.

[0007] The purpose of the present application is also to be able to greatly reduce the wind noise without affecting the drying speed, reduce the overall power consumption of the machine, improve the energy efficiency, and achieve a better balance among the drying speed, power consumption, and wind noise of the clothes dryer, making the clothes dryer more power-saving.

[0008] The purpose of the present application is also to provide a clothes dryer with a wind impeller having a relatively small size.

[0009] The purpose of the present application is not limited to the above-mentioned purposes, and those skilled in the art can clearly understand other purposes not mentioned through the following descriptions.

[0010] The clothes dryer of the present application for achieving the above purposes includes a housing.

[0011] The clothes dryer includes a drum. The drum is rotatably arranged inside the housing.

[0012] The dryer includes a base. The base is disposed inside the housing, and the drum is provided on one side of the base facing the top of the housing.

[0013] The dryer includes a motor. The motor is disposed inside the base and is connected to the drum. The motor is configured to be able to drive the drum to rotate relative to the housing.

[0014] The dryer includes a wind guide plate. The wind guide plate is installed outside the housing, and a volute is provided inside the wind guide plate. The volute is connected to the inside of the drum.

[0015] The dryer includes a wind impeller. At least part of the wind impeller is disposed inside the volute and is connected to the inside of the base. The wind impeller is connected to the motor and rotates under the drive of the motor to generate an air flow. The volute is configured to be able to direct the air flow generated by the wind impeller into the drum to dry the object to be dried inside the drum.

[0016] The dryer includes an evaporator and a condenser. Both the evaporator and the condenser are located inside the base. The evaporator is configured to be able to condense the flowing air flow when the air flow heated by drying the object to be dried enters the base, so that the air flow precipitates moisture. The condenser is configured to heat the condensed air flow, and the air flow heated by the condenser can enter the drum again via the wind impeller and the volute.

[0017] Wherein, the outer diameter of the wind impeller is greater than 130 mm and less than 140 mm, and the inner diameter of the wind impeller is greater than 100 mm and less than 110 mm.

[0018] In the embodiment of the present application, by limiting the value range of the outer diameter of the wind impeller, the overall size of the wind impeller can be reduced. In this way, when the installation position of the wind impeller in the volute and the size of the volute remain unchanged, the gap between the wind impeller and the volute can be increased. In particular, the gap between the wind impeller and the volute tongue at the end facing the wind impeller can be increased, effectively avoiding the occurrence of eddy currents in the transition section of the volute tongue in the air flow generated by the wind impeller. Thus, the air flow generated by the wind impeller will not have a large speed change when flowing through the transition section, ensuring the smoothness of the air flow, and avoiding the energy loss caused by the eddy current flowing back into the wind impeller when the air flow flows through the transition section, and the efficiency of the wind impeller is improved. In this way, when ensuring that the effective air volume output of the wind impeller remains unchanged, the work done by the motor to drive the wind impeller is less, the power consumption is smaller, and it is more energy-efficient. The power of the motor can be reduced, and the power and power consumption of the whole machine are both reduced. And, since the occurrence of eddy currents in the transition section of the air flow generated by the wind impeller is avoided, the air flow generated by the wind impeller can normally enter the drum via the air outlet end when flowing through the transition section, and will not locally circle at the transition section of the volute tongue, greatly reducing the wind noise. When the power consumption of the whole machine is reduced and the wind noise is reduced, the energy efficiency of the dryer can be improved.

[0019] Since the inner diameter of the wind impeller determines the air intake of the wind impeller. When the inner diameter of the wind impeller is relatively large, the air intake of the wind impeller increases. When the inner diameter of the wind impeller is relatively small, the air intake of the wind impeller decreases, which may lead to insufficient air intake of the wind impeller and affect the drying speed. Moreover, on the basis that the outer diameter of the wind impeller remains unchanged, when the inner diameter of the wind impeller is relatively large, it will also cause the size of the blades in the wind impeller to decrease (the blades become narrower) along the radial direction of the wind impeller. The blades are constantly stirring the air, making it difficult for the air in the wind impeller to be thrown out between adjacent blades, resulting in a decrease in the flow rate of the air flow generated by the wind impeller (a decrease in the air volume), and the same will generate relatively large wind noise.

[0020] Compared with the wind impeller with an outer diameter between 155 - 160 mm in the related art, when the outer diameter of the wind impeller in the embodiment of the present application is greater than 130 mm and less than 140 mm, and the inner diameter of the wind impeller takes a value between 100 - 110 mm, through the cooperation of the outer diameter and the inner diameter of the wind impeller, a relatively large air flow rate can be generated by the wind impeller, and while not affecting the drying speed, the wind noise can be reduced.

[0021] Therefore, the present application limits the values of the outer diameter and the inner diameter of the wind impeller. After ensuring that the size of the wind impeller is reduced, compared with the large - size outer - diameter wind impeller in the related art, while not affecting the drying speed, the wind noise can be greatly reduced, the efficiency of the wind impeller is improved, the overall power consumption of the machine is reduced, the energy efficiency is improved, and a better balance can be achieved among the drying speed, power consumption, and wind noise of the dryer.

[0022] The dryer of the present application for achieving the above - mentioned purpose includes a housing.

[0023] The dryer includes a drum. The drum is rotatably arranged inside the housing.

[0024] The dryer includes a base. The base is arranged inside the housing, and the drum is arranged on one side of the base facing the top of the housing.

[0025] The dryer includes a motor. The motor is arranged inside the base and is connected to the drum. The motor is configured to be able to drive the drum to rotate relative to the housing.

[0026] The dryer includes a guide vane. The guide vane is installed outside the housing, and a volute is provided inside the guide vane. The volute is communicated with the inside of the drum. The volute includes:

[0027] A volute body, the volute body includes a spiral section and an extension section; the spiral section defines an accommodation cavity that can accommodate the wind impeller.

[0028] One end of the spiral section is connected to the extension section;

[0029] The volute tongue includes a transition section and a diffuser section. The transition section is arc-shaped. One end of the spiral section is connected to one end of the transition section, the other end of the transition section is connected to the diffuser section, and the diffuser section and the extension section define the air outlet end of the volute casing.

[0030] The dryer includes a blower wheel. At least a part of the blower wheel is disposed in the accommodating cavity. In the radial direction of the blower wheel, the minimum distance between the blower wheel and the transition section is greater than 0.07 times and less than 0.09 times the outer diameter of the blower wheel. The blower wheel is internally connected to the base. The blower wheel is connected to the motor and rotates under the drive of the motor to generate an air flow. The air flow flows out from the air outlet end and enters the cylinder to heat the object to be dried in the cylinder.

[0031] The dryer includes an evaporator and a condenser. Both the evaporator and the condenser are located in the base. The evaporator is configured to condense the flowing air flow when the air flow heated by the object to be dried enters the base, so that the air flow precipitates moisture. The condenser is configured to heat the condensed air flow, and the air flow heated by the condenser can enter the cylinder again through the blower wheel and the volute casing.

[0032] Compared with other parts of the volute tongue, the transition section is closer to the blower wheel. The gap between the blower wheel and the transition section has a certain impact on both the efficiency and the wind noise of the blower wheel.

[0033] If the minimum distance between the blower wheel and the transition section is too close in the radial direction of the blower wheel, it will cause the air flow generated by the blower wheel to be difficult to be thrown out tangentially and flow to the air outlet end of the volute casing, which will lead to a decrease in the efficiency of the blower wheel. Moreover, since the air flow is difficult to be thrown out and flow to the air outlet end of the volute casing, the wind noise generated by the air flow at the position where the blower wheel is at a small distance from the transition section or the spiral section will increase locally.

[0034] If the minimum distance between the blower wheel and the transition section is infinitely large in the radial direction of the blower wheel, although the above problem of local increase in wind noise can be improved, it will cause the guiding effect of the volute casing on the air flow generated by the blower wheel to be very weak, and the air flow generated by the blower wheel will disperse everywhere and be difficult to be guided along the spiral section from the position of the volute tongue to the air outlet end along the guide of the volute casing, which will also lead to a decrease in the efficiency of the blower wheel.

[0035] Therefore, by defining the minimum distance between the wind impeller and the transition section in the embodiments of the present application, the minimum distance between the wind impeller and the transition section can be controlled within a more appropriate range, which can avoid the generation of eddy currents in the transition section by the airflow generated by the wind impeller, ensure that the wind impeller has a higher efficiency, and at the same time can avoid the local increase of wind noise. Without changing the effective air volume output of the wind impeller, due to the higher efficiency of the wind impeller, the work done by the motor to drive the wind impeller will be less, the power consumption will be smaller, and it will be more energy-efficient. The power of the motor can be appropriately reduced, and the power and power consumption of the whole machine are both reduced, so that a better balance can be achieved among the drying speed, power consumption, and wind noise of the dryer. When the power of the whole machine is reduced and the wind noise is reduced, the energy efficiency of the dryer can be improved.

[0036] In some embodiments, the side where the transition section is connected to the other end of the spiral section is defined as the connection side, and the connection side is located on the side of the transition section facing the wind impeller.

[0037] In the radial direction of the wind impeller: the distance between the wind impeller and the connection side is less than the distance between the wind impeller and the rest of the transition section, and the distance between the wind impeller and the connection side is also less than the distance between the wind impeller and the spiral section. That is to say, in the radial direction of the wind impeller, the distance between the wind impeller and the connection side is the minimum distance between the wind impeller and the transition section and the spiral section. This distance is equal to the above-mentioned minimum distance.

[0038] By defining the distance between the wind impeller and the connection side and the spiral section, the minimum distance between the wind impeller and the spiral section can be controlled within a more appropriate range, avoiding the influence of the too-close distance between the spiral section and the wind impeller on the efficiency and wind noise of the wind impeller, and further avoiding the local increase of wind noise, so that the efficiency of the wind impeller can be further improved.

[0039] In some embodiments, the outer diameter of the wind impeller is greater than 130 mm and less than 140 mm, and the inner diameter of the wind impeller is greater than 100 mm and less than 110 mm. With such a setting, without changing the installation position of the wind impeller in the volute and the size of the volute, the distance between the wind impeller and the connection side can be made greater than 0.07 times the outer diameter of the wind impeller and less than 0.09 times the outer diameter D1 of the wind impeller.

[0040] In some embodiments, the wind impeller includes:

[0041] A plurality of blades, arranged at intervals along the circumferential direction of the wind impeller.

[0042] The outlet angle of each blade is greater than 150° and less than 160°.

[0043] By limiting the value range of the outlet angle of each blade, the outlet angle of each blade has a good fit with the outer diameter and inner diameter of the impeller, which can ensure that the wind impeller can generate a large air flow rate, improve the efficiency of the wind impeller, so that after the outer diameter of the wind impeller is reduced, the drying speed will not be affected. At the same time, it can also avoid the generation of wind noise due to too large an outlet angle, so that a better balance can be achieved among the drying speed, power consumption and wind noise of the dryer.

[0044] In some embodiments, the inlet angle of each blade is greater than 55° and less than 65°.

[0045] By limiting the value range of the inlet angle of each blade, the shape of the blade can be adapted to the dimensions of the outer diameter and inner diameter of the wind impeller, so that the air duct defined by adjacent blades has good air inlet and outlet effects, ensuring that the wind impeller can generate a large air flow rate, further improving the efficiency of the wind impeller, so that after the outer diameter of the wind impeller is reduced, the drying speed of the wind impeller will not be affected, and further enhancing the balance among the drying speed, power consumption and wind noise of the dryer.

[0046] In some embodiments, the number of blades is greater than 33 and less than 39.

[0047] By limiting the value range of the number of blades, the number of blades can be matched with the diameter of the wind impeller, so as to further reduce the wind noise generated by the wind impeller and further enhance the balance among the drying speed, power consumption and wind noise of the dryer.

[0048] In some embodiments, the wind impeller includes a wind impeller chassis. The wind impeller chassis is configured to be connected to the motor.

[0049] In some embodiments, the wind impeller includes a wind impeller outer edge. The wind impeller outer edge is spaced apart from the wind impeller chassis along the axial direction of the wind impeller.

[0050] A plurality of blades are spaced apart circumferentially along the wind impeller chassis, and along the axial direction of the wind impeller, one end of each blade is connected to the wind impeller chassis, and the other end is connected to the wind impeller outer edge to realize the installation of the blades on the wind impeller.

[0051] In some embodiments, the wind impeller has an outlet. The outlet is formed on the circumferential side of the wind impeller chassis, and the diameter of the wind impeller chassis constitutes the inner diameter of the outlet.

[0052] The diameter of the wind impeller chassis is greater than 108 mm and less than 115 mm.

[0053] By limiting the size of the diameter of the wind impeller chassis, the strength of the wind impeller can be improved, so as to further avoid the deformation of the wind impeller at a higher temperature and ensure the structural stability of the wind impeller.

[0054] In some embodiments, the outer edge of the wind impeller also has a reinforcing portion on the side facing the blade, and the surface of the reinforcing portion facing the blade has a concave surface.

[0055] A part of the blade is disposed within the concave surface and is connected to the concave surface.

[0056] Compared with the planar design of the surface of the reinforcing portion facing the blade, when the surface of the reinforcing portion facing the blade is a concave surface, while strengthening the strength of the outer edge of the wind impeller through the reinforcing portion, the outer edge of the wind impeller can also be thinned. And, through the setting of the concave surface, it is also possible to minimize the influence of the presence of the reinforcing portion on the flow rate of the air flow generated by the wind impeller.

[0057] In some embodiments, the reinforcing portion is an annular structure. The concave surface includes a bottom wall and two side walls. The two side walls are symmetrically disposed on both sides of the bottom wall. The two side walls are both connected to the bottom wall and together with the bottom wall enclose an annular groove.

[0058] A part of the blade is disposed within the annular groove and is connected to the bottom wall, so that a part of the blade can be located within the concave surface and is connected to the concave surface.

[0059] Since the bottom wall and the two side walls of the concave surface together enclose an annular groove, the cross-section of the outer edge of the wind impeller at the reinforcing portion can be a "U" - shaped structure, or other structures with two symmetric side walls similar to the "U" - shaped structure. Through a large number of experimental verifications, compared with the two side walls on both sides of the bottom wall being asymmetric structures, when the reinforcing portion is an annular structure and the cross-section of the outer edge of the wind impeller at the reinforcing portion is a "U" - shaped structure or other structures with two symmetric side walls similar to the "U" - shaped structure, while minimizing the influence of the presence of the reinforcing portion on the flow rate of the air flow generated by the wind impeller, it is also possible to reduce the wind noise.

[0060] In some embodiments, the axial thickness of the wind impeller is greater than 40 mm and less than 45 mm.

[0061] By limiting the axial thickness of the wind impeller, the axial thickness of the wind impeller can be controlled within a more appropriate range, so that the axial thickness of the wind impeller matches the diameter (inner diameter and outer diameter) of the wind impeller, to avoid the axial thickness of the wind impeller affecting the flow rate of the air flow generated by the wind impeller, and can further enhance the balance among the drying speed, power consumption, and wind noise of the dryer. At the same time, it can also avoid the weakening of the strength of the wind impeller.

[0062] In some embodiments, each wind impeller has an inlet in the axial direction. The diameter of the inlet is greater than 110 mm and less than 115 mm.

[0063] By limiting the value of the diameter of the inlet, it is possible to enable the wind impeller to have a relatively large air intake, ensuring that the flow rate of the air flow generated by the wind impeller is basically unaffected. While further enhancing the balance among the drying speed, power consumption, and wind noise of the dryer, it is also possible to avoid having too much impact on the strength of the wind impeller, making the structure of the wind impeller relatively stable and not easily deformed at a relatively high temperature. BRIEF DESCRIPTION OF THE DRAWINGS

[0064] In order to more clearly illustrate the embodiments of the present application or the implementation manners in the related art, the following will briefly introduce the drawings required for use in the description of the embodiments or the related art. Obviously, the drawings in the following description are some embodiments of the present application. For those of ordinary skill in the art, other drawings can also be obtained based on these drawings.

[0065] Figure 1 is a schematic structural diagram of a dryer provided by an embodiment of the present application;

[0066] Figure 2 is a partial exploded view of a dryer provided by an embodiment of the present application;

[0067] Figure 3 is a schematic installation diagram of a wind impeller on a wind guide plate;

[0068] Figure 4 is a schematic diagram of the flow direction of the air flow in the dryer;

[0069] Figure 5 is a wind noise spectrogram of a dryer in the related art;

[0070] Figure 6 is a real-time wind noise spectrogram of a dryer in the related art;

[0071] Figure 7 is a streamline diagram of a wind impeller in the related art;

[0072] Figure 8 is a noise diagram of a wind impeller in the related art;

[0073] Figure 9 is a schematic structural diagram of a wind impeller provided by an embodiment of the present application from a first perspective;

[0074] Figure 10 is Figure 9 a schematic structural diagram of the wind impeller in

[0075] Figure 11 is Figure 10 a sectional view in the A-A direction;

[0076] Figure 12 is Figure 9Schematic structural diagram of the air impeller in the third perspective;

[0077] Figure 13 is Figure 9 Schematic structural diagram of the air impeller in the fourth perspective;

[0078] Figure 14 is Figure 13 Partial sectional view in the B - B direction;

[0079] Figure 15 is Figure 12 Enlarged view at C.

[0080] Reference numerals:

[0081] 100 - Dryer;

[0082] 10 - Cylinder body;

[0083] 20 - Base module;

[0084] 21 - Base; 22 - Motor; 23 - Heat exchanger; 231 - Evaporator; 232 - Condenser;

[0085] 30 - Belt;

[0086] 40 - Air deflector;

[0087] 41 - Volute; 411 - Volute body; 4111 - Spiral section; 4112 - Extension section; 412 - Volute tongue; 4121 - Transition section; 4122 - Diverging section; 4123 - Joining edge;

[0088] 50 - Rear panel;

[0089] 60 - Air impeller;

[0090] 61 - Blade; 611 - Horizontal section; 62 - Air duct; 63 - Air impeller chassis; 64 - Air impeller outer edge; 641 - Reinforcing part; 6411 - Concave surface; 6412 - Bottom wall; 6413 - Side wall; 6414 - Annular groove; 65 - Inlet; 66 - Outlet. Detailed implementation manners

[0091] To make the purpose, implementation manners and advantages of this application clearer, the following will clearly and completely describe the exemplary implementation manners of this application in combination with the drawings in the exemplary embodiments of this application. Obviously, the described exemplary embodiments are only a part of the embodiments of this application, rather than all of the embodiments.

[0092] The embodiments of this application provide a dryer. The dryer may include a heat pump dryer or other devices capable of drying the objects to be dried. For example, the objects to be dried may be clothes, trousers, socks, blankets, etc.

[0093] The dryer may include a housing. The housing has an opening for loading and unloading clothes.

[0094] The dryer may include a door. The door is rotatably connected to the housing and is configured to cover the opening for loading and unloading clothes when rotated to the opening for loading and unloading clothes.

[0095] Figure 1 A schematic structural diagram of a dryer is schematically shown.

[0096] See Figure 1 As shown, the dryer 100 may include a cylinder 10. The cylinder 10 may be rotatably disposed within the housing. When the cylinder 10 rotates relative to the housing, the wet objects to be dried within the cylinder 10 can be tumbled back and forth within the cylinder 10, so as to facilitate the rapid drying of the objects to be dried.

[0097] When the cylinder 10 is disposed within the housing, the axial direction of the cylinder 10 may be parallel to the thickness direction of the dryer 100, and the mouth of the cylinder 10 may face the opening for loading and unloading clothes, so that when the door rotates relative to the housing and opens, the objects to be dried can be put into the cylinder 10 through the opening for loading and unloading clothes, so as to dry the objects to be dried through the dryer 100.

[0098] It should be noted that the thickness direction of the dryer 100 may refer to the X direction.

[0099] The dryer 100 may include a base module 20. The base module 20 may be disposed within the housing. The base module 20 may include a base 21 and a motor 22. The base 21 may be disposed within the housing, and the motor 22 may be disposed within the base 21. The cylinder 10 may be disposed on one side of the base 21 facing the top of the housing, and a belt 30 may be wound around the circumference of the cylinder 10. Driven by the motor 22, the belt 30 can drive the cylinder 10 to rotate, so that the cylinder 10 can rotate relative to the housing under the drive of the belt 30, enabling the wet objects to be dried within the cylinder 10 to be tumbled back and forth within the cylinder 10.

[0100] It should be noted that when the dryer 100 is placed on a placement platform, along the height direction of the dryer 100, the end of the housing adjacent to the placement platform may be understood as the bottom of the housing, and the end of the housing far from the placement platform may be understood as the top of the housing. The height direction of the dryer 100 may refer to the Z direction.

[0101] See Figure 2As shown, in some embodiments, the dryer 100 may further include a wind guide plate 40. The wind guide plate 40 may be installed outside the housing. The wind guide plate 40 may have a volute 41 therein. Among them, the volute 41 may be provided on the side of the wind guide plate 40 facing the housing. The volute 41 may be communicated with the inside of the cylinder 10, so that the air flow in the volute 41 can flow into the inside of the cylinder 10 to take away the moisture in the object to be dried in the cylinder 10, thereby realizing the drying of the object to be dried.

[0102] The volute 41 may include a volute body 411 and a volute tongue 412. The volute body 411 includes a spiral section 4111 and an extension section 4112. The spiral section 4111 defines a receiving cavity that can accommodate the wind impeller 60, and the extension section 4112 is connected to one end of the spiral section 4111. The volute tongue 412 may include a transition section 4121 and a diverging section 4122. The transition section 4121 is arc-shaped, and one end of the transition section 4121 is connected to the other end of the spiral section 4111. The diverging section 4122 is connected to the other end of the transition section 4121, and the diverging section 4122 and the extension section 4112 define the air outlet end of the volute 41.

[0103] When the wind guide plate 40 is installed outside the housing, the wind guide plate 40 may be installed at one end of the housing in the thickness direction of the dryer 100. Among them, along the thickness direction of the dryer 100, the door body and the wind guide plate 40 may be installed at opposite ends of the housing. For example, the door body may be provided at the front end of the housing, and the wind guide plate 40 may be installed on the rear back plate 50 of the housing at the rear end. A communication port may be provided on the back plate 50, and the communication port may be communicated with the inside of the cylinder 10 and the volute 41, so that the volute 41 can be communicated with the inside of the cylinder 10 through the communication port.

[0104] It should be noted that when the user uses the dryer 100, the end of the housing facing the user in the thickness direction of the dryer 100 may be understood as the front end of the housing, and the end of the housing away from the user in the thickness direction of the dryer 100 may be understood as the rear end of the housing.

[0105] Figure 2 Shows Figure 1 A partial exploded view of the dryer 100 in

[0106] See Figure 2 As shown, in some embodiments, the dryer 100 may further include a wind impeller 60.

[0107] Figure 3 Schematically shows an installation schematic diagram of the wind impeller 60 on the wind guide plate 40.

[0108] See Figure 3As shown, at least a part of the wind impeller 60 can be disposed inside the volute 41. For example, in some embodiments, the wind impeller 60 can be entirely disposed inside the accommodating cavity of the volute 41. Alternatively, in some other embodiments, a part of the wind impeller 60 can be disposed inside the accommodating cavity of the volute 41, and a part can be disposed inside the housing.

[0109] The wind impeller 60 is configured to be connectable to the motor 22 and rotate under the drive of the motor 22 to generate an air flow. The volute 41 is configured to direct the air flow generated by the wind impeller 60 into the cylinder 10 to dry the object to be dried inside the cylinder 10, thereby realizing the drying function of the dryer 100 for the object to be dried inside the cylinder 10. For example, when the wind impeller 60 rotates, the air flow inside the housing can enter the wind impeller 60, and an air flow is generated between the adjacent blades 61 of the wind impeller 60. The generated air flow can flow out from the air outlet end of the volute 41 and enter the cylinder 10 to dry the object to be dried inside the cylinder 10.

[0110] Since the air outlet end of the volute 41 is a part of the volute 41, when the volute 41 is connected to the inside of the cylinder 10 through the communication port, the air outlet end of the volute 41 can be connected to the inside of the cylinder 10 through the communication port, so that the air flow generated between the adjacent blades 61 of the wind impeller 60 can flow out from the air outlet end of the volute 41 and enter the cylinder 10 to dry the object to be dried inside the cylinder 10.

[0111] Figure 4 Schematically shows a schematic diagram of the air flow direction inside the dryer 100.

[0112] See Figure 4 As shown, in some embodiments, the base module 20 of the dryer 100 can further include a heat exchanger 23. The heat exchanger 23 can be located inside the base 21. When the dryer 100 is in the working state, the motor 22 rotates and drives the wind impeller 60 to rotate to generate an air flow, and the air flow can be hot air. After the air flow passes through the volute 41 of the air guide plate 40, it can enter the cylinder 10 through the communication port on the rear back plate 50. At this time, the object to be dried inside the cylinder 10 can tumble and be shaken loose under the rotation of the cylinder 10. When the air flow generated by the wind impeller 60 flows through the inside of the cylinder 10, it can heat the wet object to be dried, and after heating, it can flow out from one end of the cylinder 10 facing the door body and enter the base 21. When the air flow entering the base 21 flows through the heat exchanger 23, the heat exchanger 23 can condense and precipitate moisture from the air flow and heat the air flow. The heated air flow can then pass through the wind impeller 60 again, enter the volute 41 and the cylinder 10 through the wind impeller 60 to dry the object to be dried. At the same time, an internal circulation of the air flow inside the dryer 100 is formed.

[0113] The heat exchanger 23 may include an evaporator 231 and a condenser 232. The air flow entering the base 21 may first flow through the evaporator 231, and when flowing through the evaporator 231, moisture can be condensed and separated out near the evaporator 231, and then enter the condenser 232. The air flow can be heated by the condenser 232 so that when the air flow enters the cylinder body 10 again, it can continue to heat the wet object to be dried. Thus, through the continuous internal circulation of the air flow in the dryer 100, the object to be dried can be dried.

[0114] It should be understood that in order to make the air flow flow out from one end of the cylinder body 10 towards the door body and enter the base 21 after heating the object to be dried, the inside of the base 21 is also communicated with one end of the cylinder body 10 towards the door body.

[0115] Similarly, it should be understood that in order to make the air flow heated by the condenser 232 enter the cylinder body 10 again via the air impeller 60 and the volute 41, in addition to the volute 41 being communicated with the inside of the cylinder body 10, the air impeller 60 is also communicated with the base 21.

[0116] With the progress of technology, people have put forward higher requirements for the energy efficiency, power, etc. of the dryer 100. For the dryer 100, the energy efficiency is a comprehensive index, which includes indexes such as washing effect, energy saving, and wind noise. The power of the dryer 100 refers to the speed at which thermal energy is converted into mechanical energy, electrical energy or thermal energy, and is usually measured in kilowatts (kW). The higher the power of the dryer 100, the more heat the wet object to be dried absorbs, and the faster the drying speed. However, a higher power does not necessarily mean better drying, because if the objects to be dried in the cylinder body 10 are thinner, less, or the material has little influence on the drying speed, a dryer 100 with a lower power is more suitable. Moreover, compared with high-power dryers, low-power dryers not only have an economical price, but also have the characteristics of less power consumption, making the dryer 100 have the characteristics of energy saving, which is beneficial to improving the energy efficiency of the dryer 100.

[0117] The internal circulation of the air flow in the dryer 100 is the basic condition for the dryer 100 to dry. The power source of the internal circulation of the air flow in the dryer 100 comes from the air impeller 60. The dimensional parameters of the air impeller 60 determine the circulation speed of the internal air, and thus affect the drying speed. For example, the larger the outer diameter of the impeller size, the larger the air flow rate (such as the air volume) generated, and the faster the drying speed. However, at the same time, it will also bring greater wind noise, increase power consumption, and affect the energy efficiency and user experience of the dryer 100.

[0118] For example, in the related art, the air impellers of dryers mostly use forward-inclined centrifugal air impellers. The outer diameter of the forward-inclined centrifugal air impeller is usually between 155 and 160 mm, and the axial thickness is usually between 50 and 60 mm. When using such an air impeller in a dryer, at a fixed-frequency motor speed of 2800 rpm, the air flow rate generated by the air impeller basically remains between 230 and 250 m 3 / h. Although such an air impeller can generate a large air flow rate and improve the drying speed, at the same time, it will increase the power and power consumption of the dryer. Moreover, the air impeller will generate a large amount of wind noise during rotation, making the overall experience of the dryer not friendly. It should be understood that when the power and power consumption of the dryer increase, the power consumption of the dryer will be relatively large.

[0119] Therefore, it is necessary to balance the drying speed, power consumption, and wind noise of the dryer. And how to balance the drying speed, power consumption, and wind noise of the dryer has become a technical problem to be solved.

[0120] It should be noted that the forward-inclined centrifugal air impeller refers to a fan in which air exits from the circumference of the air impeller and generates an air flow. For specific details, reference can be made to the description of the forward-inclined centrifugal air impeller in the prior art, which will not be elaborated further here.

[0121] For this reason, the inventors of this application simulated the entire dryer in the related art to analyze the wind noise.

[0122] Figure 5 shows a wind noise spectrogram of a dryer 100 in the related art, Figure 6 shows a real-time wind noise spectrogram of a dryer in the related art. Among them, Figure 5 is Figure 6 the wind noise spectrogram of the dryer in a certain fixed moment.

[0123] See Figure 5 As shown, the wind noise of the dryer in the related art is relatively obvious at a fixed moment.

[0124] Normally, along the direction of gradually increasing frequency ( Figure 6 from left to right in the direction shown), the color in the real-time wind noise spectrogram transitions smoothly.

[0125] See Figure 6 As shown, however, the vertical stripe where Q1 is located in the dryer in the related art does not have a smooth color transition compared to the left and right sides, which is rather abrupt. This indicates that the wind noise at the frequency corresponding to the vertical stripe where Q1 is located is relatively sharp and obvious.

[0126] Based on this, the inventors of the present application conducted a simulation analysis on the cooperation between the impeller and the volute of the air guide plate in the related art dryers to explore the source and formation mechanism of the wind noise, and then determine improvement measures.

[0127] Figure 7 Fig. shows the streamline diagram of the impeller in the related art. Figure 8 Fig. shows the noise diagram of the impeller in the related art.

[0128] See Figure 7 As shown in the figure, the simulation results show that the gap between the impeller and the volute in the related art (such as positions Q2 and Q3) is too close. In particular, the gap between the impeller and the volute tongue (position Q2) is too close, which will cause the air flow generated by the impeller to form eddy currents at the volute tongue. Specifically, it will cause the air flow generated by the impeller to form eddy currents in the transition section of the volute tongue. It should be understood that the position Q2 can be understood as the end of the volute tongue facing the impeller, that is, the transition section.

[0129] See Figure 8 As shown in the figure, due to the existence of eddy currents, the air flow generated by the impeller will have a large speed change, resulting in chaotic flow of the air flow at the air outlet end and the volute tongue of the volute, causing energy loss, and further resulting in a large power of the impeller and generating a large wind noise.

[0130] Specifically, due to the existence of eddy currents, the air flow in the transition section of the volute will be chaotic, and part of the air flow may flow back into the impeller, causing energy loss. In the design of dryers, it is usually required that the effective output air volume of the impeller remains unchanged. In this way, when the energy of the impeller is lost while ensuring that the effective output air volume of the impeller remains unchanged, it will cause the impeller to do more work under the drive of the motor, resulting in a lower efficiency of the impeller, more power consumption, a larger power of the motor, and further increasing the power and power consumption of the dryer. Moreover, when the air flow passes through the end of the volute tongue facing the impeller, due to the chaotic flow, part of the air flow cannot normally enter the cylinder 10 through the air outlet end, and will locally circle at the transition section of the volute tongue, generating a large wind noise.

[0131] Based on the above analysis, the present application adjusts and optimizes the parameters of the impeller 60. Without affecting the drying speed, it can greatly reduce the overall wind noise of the machine, and at the same time can reduce the overall power consumption and improve the energy efficiency of the dryer 100, so that a better balance can be achieved among the drying speed, power consumption and wind noise of the dryer 100.

[0132] The following further elaborates on the parameters of the impeller 60 of the present application in conjunction with the drawings and embodiments.

[0133] Figure 9 Fig. schematically shows a structural diagram of an impeller 60 from a first perspective.

[0134] SeeFigure 9 As shown, in the embodiment of the present application, the outer diameter D1 of the impeller 60 of the dryer 100 can be greater than or equal to 130 mm and less than or equal to 140 mm. That is to say, the outer diameter D1 of the impeller 60 can take values between 130 - 140 mm. For example, the outer diameter D1 of the impeller 60 can be 130 mm, 132 mm, 135 mm, 136 mm, 138 mm, 140 mm, etc.

[0135] Compared with the outer diameter of the impeller in the related technology mentioned above, which is between 155 - 160 mm, in the embodiment of the present application, by limiting the size of the outer diameter D1 of the dryer 100, the outer diameter of the impeller 60 is reduced, and the overall size of the impeller 60 is reduced. In this way, when the installation position of the impeller 60 in the volute 41 and the size of the volute 41 remain unchanged, the gap between the impeller 60 and the volute 41 can be increased. In particular, the gap between the impeller 60 and the volute tongue 412 of the volute 41 is increased, effectively avoiding the eddy current generated by the airflow of the impeller 60 at the volute tongue 412 due to the too-close gap between the impeller 60 and the volute 41. As a result, the airflow generated by the impeller 60 will not have a large speed change when flowing through the volute tongue 412, ensuring the smoothness of the airflow, avoiding energy loss, thus greatly reducing the wind noise. At the same time, the power of the impeller 60 is also reduced, which can reduce the overall power consumption of the dryer 100 and improve the energy efficiency of the dryer 100.

[0136] See Figure 9 As shown, when the outer diameter D1 of the impeller 60 is greater than or equal to 130 mm and less than or equal to 140 mm, the inner diameter D2 of the impeller 60 can be greater than or equal to 100 mm and less than or equal to 110 mm. That is to say, the inner diameter D2 of the impeller 60 can take values between 100 - 110 mm. For example, the inner diameter D2 of the impeller 60 can be 100 mm, 102 mm, 103 mm, 105 mm, 105.7 mm, 106 mm, 108 mm, 140 mm, etc.

[0137] Since the inner diameter D2 of the impeller 60 determines the air intake of the impeller 60. When the inner diameter D2 of the impeller 60 is relatively large, the air intake of the impeller 60 increases. When the inner diameter D2 of the impeller 60 is relatively small, the air intake of the impeller 60 decreases, which may lead to insufficient air intake of the impeller 60 and affect the drying speed. Moreover, on the basis of the unchanged outer diameter D1 of the impeller 60, when the inner diameter D2 of the impeller 60 is relatively large, it will also cause the size of the blades 61 in the impeller 60 to decrease (the blades 61 become narrower) along the radial direction of the impeller 60. The blades 61 are always stirring the air, making it difficult for the air in the impeller 60 to be thrown out between adjacent blades 61, resulting in a decrease in the flow rate of the airflow generated by the impeller 60 (the air volume decreases), and the same will generate relatively large wind noise.

[0138] Compared with the wind impeller with an outer diameter between 155 - 160 mm in the related art, in the embodiment of the present application, when the outer diameter D1 of the wind impeller 60 is greater than or equal to 130 mm and less than or equal to 140 mm, and the inner diameter D2 of the wind impeller 60 takes a value between 100 - 110 mm, while ensuring the air intake volume of the wind impeller 60, the outer diameter D1 of the wind impeller 60 is matched, which can make the wind impeller 60 generate a large air flow rate, reduce wind noise while not affecting the drying speed.

[0139] Therefore, by limiting the values of the outer diameter D1 and the inner diameter D2 of the wind impeller 60, the present application ensures that after the size of the wind impeller 60 is reduced, compared with the wind impeller 60 with a large outer diameter in the related art, while not affecting the drying speed, it can greatly reduce the wind noise, and the power of the wind impeller 60 and the overall power consumption of the machine are also reduced, improving the energy efficiency, and enabling a better balance among the drying speed, power consumption, and wind noise of the dryer 100.

[0140] Verified by experiments, compared with the dryer using the wind impeller with an outer diameter between 155 - 160 mm mentioned above, after optimizing the outer diameter D1 and the inner diameter D2 of the wind impeller 60 in the embodiment of the present application, the overall power of the dryer 100 is reduced by at least 15 w, reducing the energy consumption of the dryer 100, making the dryer 100 more power - saving. At the same time, the wind noise of the dryer 100 is reduced by at least 3 dB, greatly improving the user experience.

[0141] It should be noted that the wind impeller 60 intakes air from its own axial direction, discharges air from the circumferential direction and forms an air flow. The axial direction of the wind impeller 60 can be parallel to the X direction mentioned above (see Figure 1 ).

[0142] Figure 10 Schematically shows Figure 9 the structural schematic diagram of the wind impeller 60 in the second perspective in

[0143] See Figure 9 and Figure 10 As shown, in some embodiments, the wind impeller 60 may further include a plurality of blades 61. The plurality of blades 61 are arranged at intervals along the circumferential direction of the wind impeller 60. A wind channel 62 can be formed between adjacent blades 61. After the wind intakes from the axial direction of the wind impeller 60, it can discharge from the wind channel 62 formed between two adjacent blades 61 to achieve the circumferential air discharge and form an air flow of the wind impeller 60.

[0144] Figure 11 Schematically shows Figure 10 the cross - sectional view in the A - A direction in

[0145] See Figure 11As shown, in some embodiments, the outlet angle β1 of each blade 61 may be greater than or equal to 150° and less than or equal to 160°. That is to say, the outlet angle β1 of each blade 61 may take values between 150° and 160°. For example, the outlet angle β1 of the wind impeller 60 may be 150°, 152°, 153°, 154°, 154.6°, 155°, 157°, 158°, etc.

[0146] It should be noted that the circumcircle of the multiple blades 61 intersects each blade 61. At the intersection of each blade 61 and the circumcircle, the included angle formed by the tangent of the blade 61 passing through this intersection and the tangent of the circumcircle passing through this point is the outlet angle β1 of the blade 61.

[0147] When the dimensions of the outer diameter D1 and the inner diameter D2 of the wind impeller 60 are determined, the approximate range of the air flow rate (air volume) that the wind impeller 60 can generate has been basically determined. However, the outlet angle β1 of the blade 61 will also affect the air flow rate generated by the wind impeller 60.

[0148] For example, when the outlet angle β1 of the blade 61 is relatively large, the air flow rate generated by the wind impeller 60 increases. However, the efficiency of the wind impeller 60 will decrease and the generated wind noise will increase.

[0149] Again, for example, when the outlet angle β1 of the blade 61 is relatively small, the air flow rate generated by the wind impeller 60 decreases, and the air flow rate is insufficient, affecting the drying speed and drying effect.

[0150] Therefore, when the outer diameter D1 and the inner diameter D2 of the wind impeller 60 take values within the above ranges, and the outlet angle β1 of each blade 61 can take values between 150° and 160°, the outlet angle β1 of each blade 61 can be controlled within a more appropriate range, and has a better matching degree with the outer diameter D1 and the inner diameter D2 of the impeller, so that the air duct 62 defined by adjacent blades 61 has a better air outlet effect. This can ensure that the wind impeller 60 can generate a large air flow rate, improve the efficiency of the wind impeller 60, so that after the outer diameter D1 of the wind impeller 60 is reduced, it will not affect the drying speed, and at the same time, it can avoid the generation of wind noise due to the relatively large outlet angle β1, so that a better balance can be achieved among the drying speed, power consumption, and wind noise of the dryer 100.

[0151] See Figure 11 As shown, in some embodiments, the inlet angle β2 of each blade 61 may be greater than or equal to 55° and less than or equal to 65°. That is to say, the inlet angle β2 of each blade 61 may take values between 55° and 65°. For example, the inlet angle β1 of the wind impeller 60 may be 55°, 57°, 60°, 61°, 63°, 64°, etc.

[0152] It should be noted that the inscribed circle of the multiple blades 61 intersects with each blade 61. At the intersection of each blade 61 and the inscribed circle, the included angle formed by the tangent of the blade 61 passing through this intersection and the tangent of the inscribed circle passing through this point is the inlet angle β2 of the blade 61.

[0153] The inlet angle β2 and the outlet angle β1 of the blade 61 determine the shape of the blade 61. That is to say, after the inlet angle β2 and the outlet angle β1 of the blade 61 are determined, the shape of the blade 61 is basically determined.

[0154] When the outer diameter D1 and the inner diameter D2 of the wind impeller 60 take values within the above ranges, and the outlet angle β1 of the blade 61 takes a value between 150° - 160°, and the inlet angle β2 of the blade 61 takes a value between 55° - 65°, it can make the shape of the blade 61 adapt to the dimensions of the outer diameter D1 and the inner diameter D2 of the wind impeller 60, so that the air duct 62 defined by adjacent blades 61 has a good air inlet and outlet effect, ensuring that the wind impeller 60 can generate a large airflow rate, further improving the efficiency of the wind impeller 60, so that after the outer diameter D1 of the wind impeller 60 is reduced, it will not affect the drying speed of the wind impeller 60, and further enhancing the balance among the drying speed, power consumption and wind noise of the dryer 100.

[0155] See Figure 11 As shown, in some embodiments, the number of blades 61 can be greater than or equal to 33 and less than or equal to 39. Among them, the number of blades 61 can also be greater than or equal to 34 and less than or equal to 38. That is to say, the number of blades 61 can take values between 33 and 39. For example, the number of blades 61 can be 33, 34, 36, 38, etc.

[0156] When designing the wind impeller 60, the number of blades 61 generally matches the diameter of the wind impeller 60 (such as the outer diameter D1 and the inner diameter D2). If the number of blades 61 is too large, the arrangement of the blades 61 in the wind impeller 60 is relatively dense, and when air flows through the air duct 62 between adjacent blades 61, wind noise is likely to be generated. If the number of blades 61 is too small, the arrangement of the blades 61 in the wind impeller 60 is relatively sparse, which easily causes the airflow generated by the wind impeller 60 in the air duct 62 between adjacent blades 61 to be unstable, sometimes large and sometimes small.

[0157] When the outer diameter D1 and the inner diameter D2 of the wind impeller 60 take values within the corresponding ranges, and the number of blades 61 takes values between 33 and 39, the number of blades 61 can be controlled within a more appropriate range, so that the number of blades 61 matches the diameter of the wind impeller 60, further reducing the wind noise generated by the wind impeller 60 and further enhancing the balance among the drying speed, power consumption and wind noise of the dryer 100.

[0158] Figure 12 Shows Figure 9 a schematic structural view of the wind impeller 60 in FIG. Figure 13 is Figure 9 a schematic structural view of the wind impeller 60 in FIG.

[0159] Refer to Figure 12 and Figure 13 As shown, in some embodiments, the wind impeller 60 may include a wind impeller chassis 63. The wind impeller chassis 63 is configured to be connected to the motor 22. That is to say, the rotating shaft of the motor 22 can be installed on the wind impeller chassis 63. In this way, when the rotating shaft of the motor 22 rotates, it can drive the wind impeller 60 to rotate. The area of the wind impeller chassis 63 on the circumferential side of the motor 22 can be regarded as the sealing side of the wind impeller chassis 63.

[0160] In some embodiments, the wind impeller 60 may further include a wind impeller outer edge 64. The wind impeller outer edge 64 and the wind impeller chassis 63 may be arranged at intervals along the axial direction of the wind impeller 60. A plurality of blades are arranged at intervals along the circumferential direction of the wind impeller chassis 63, and along the axial direction of the wind impeller 60, one end of the blade is connected to the wind impeller chassis 63, and the other end is connected to the wind impeller outer edge 64 to realize the installation of the blade on the wind impeller 60.

[0161] In some embodiments, the wind impeller 60 has an inlet 65 in the axial direction so that air can enter the wind impeller 60 from the inlet 65. The air duct 62 can be communicated with the inlet 65 so that after the air enters from the inlet 65, it can enter the air duct 62 to realize the axial air intake of the wind impeller 60. The diameter D3 of the inlet 65 can be greater than or equal to 110 mm and less than or equal to 115 mm. That is to say, the diameter D3 of the inlet 65 can take values between 110 - 115 mm. For example, the diameter D3 of the inlet 65 can be 110 mm, 112 mm, 113 mm, 114 mm, etc.

[0162] It should be noted that the diameter D3 of the inlet 65 can be regarded as the inner diameter of the wind impeller outer edge 64.

[0163] The diameter D3 of the inlet 65 determines the air intake volume of the wind impeller 60 and the structural strength of the wind impeller 60. If the diameter D3 of the inlet 65 is too small, the inlet 65 decreases, the air intake volume decreases, and the airflow generated by the wind impeller 60 also decreases. If the diameter D3 of the inlet 65 is too large, the inlet 65 increases, the air intake volume increases, and the airflow generated by the wind impeller 60 also increases, but the strength of the wind impeller 60 will become weaker. When the diameter D3 of the inlet 65 is closer to the outer diameter D1, the strength of the wind impeller 60 is weaker. Since the air entering the wind impeller 60 in the dryer 100 is hot air with a relatively high temperature, if the strength of the wind impeller 60 is relatively high, the wind impeller 60 may be deformed at a relatively high temperature, affecting the structural stability of the wind impeller 60.

[0164] Therefore, compared with the wind impeller in the related art mentioned above, when the outer diameter D1 takes values within the above range and the diameter D3 of the inlet 65 takes values between 110 - 115 mm, the wind impeller 60 has a relatively large air intake volume, ensuring that the flow rate of the air flow generated by the wind impeller 60 is basically not affected. While further enhancing the balance among the drying speed, power consumption, and wind noise of the dryer 100, it can also avoid having too much impact on the strength of the wind impeller 60, making the structure of the wind impeller 60 relatively stable and not easily deformed at a relatively high temperature.

[0165] In some embodiments, the wind impeller 60 has an outlet 66, and the outlet 66 is formed on the circumferential side of the wind impeller chassis 63. Specifically, along the circumferential direction of the wind impeller 60, an outlet 66 can be defined between the circumferential side of the wind impeller chassis 63 and the wind impeller outer edge 64. The air duct 62 can be located within the outlet 66 so that the air flow within the air duct 62 can be thrown out from the outlet 66 to achieve circumferential air outlet of the wind impeller 60. The diameter D4 of the wind impeller chassis 63 constitutes the inner diameter of the outlet 66. The diameter D4 of the wind impeller chassis 63 can be greater than or equal to 108 mm and less than or equal to 115 mm. That is to say, the diameter D4 of the wind impeller chassis 63 can take values between 108 - 115 mm. For example, the diameter D4 of the wind impeller chassis 63 can be 108 mm, 110 mm, 113 mm, 114 mm, etc. By defining the size of the diameter D4 of the wind impeller chassis 63, the strength of the wind impeller 60 can be improved to further avoid the deformation of the wind impeller 60 at a relatively high temperature and ensure the stability of the structure of the wind impeller 60.

[0166] In some embodiments, the diameter D4 of the wind impeller chassis 63 can also be smaller than the diameter D3 of the inlet 65, so as to reduce the relatively large mold processing difficulty during the production of the wind impeller 60, making the wind impeller 60 easier to form and reducing the production cost of the wind impeller 60.

[0167] See Figure 10 As shown, in some embodiments, the axial thickness b of the wind impeller 60 can be greater than or equal to 40 mm and less than or equal to 45 mm. That is to say, the axial thickness b of the wind impeller 60 can take values between 40 - 45 mm. For example, the axial thickness b of the wind impeller 60 can be 40 mm, 42 mm, 43 mm, 44 mm, etc.

[0168] It should be noted that the axial thickness b of the wind impeller 60 refers to the thickness of the wind impeller 60 after removing the wall thicknesses on both sides in the axial direction. The wall thicknesses on both sides refer to the wall thickness of the wind impeller outer edge 64 of the wind impeller 60 and the wall thickness of the wind impeller 60 on the plugging side of the wind impeller chassis 63.

[0169] The axial thickness b of the wind impeller 60 affects the flow rate of the air flow generated by the wind impeller 60. When the inner diameter D2 and the outer diameter D1 of the wind impeller 60 are fixed, if the axial thickness b of the wind impeller 60 is too large, the wind is not easy to enter the wind impeller 60, and the strength of the wind impeller 60 is weakened and unstable; if the axial thickness b of the wind impeller 60 is too small, the inlet 65 of the wind impeller 60 is very large, but the outlet 66 is very small. The wind can enter the wind impeller 60, but it is difficult to be thrown out.

[0170] When the outer diameter D1 and the inner diameter D2 of the wind impeller 60 are within the corresponding value ranges, and the axial thickness b of the wind impeller 60 is within the range of 40 - 45 mm, the axial thickness b of the wind impeller 60 can be controlled within a more appropriate range, so that the axial thickness b of the wind impeller 60 matches the diameter (inner diameter D2 and outer diameter D1) of the wind impeller 60, so as to avoid the axial thickness b of the wind impeller 60 affecting the flow rate of the air flow generated by the wind impeller 60, and can further enhance the balance among the drying speed, power consumption and wind noise of the dryer 100. At the same time, it can also avoid the weakening of the strength of the wind impeller 60.

[0171] Figure 14 shows Figure 13 a partial cross-sectional view in the B - B direction. Refer to Figure 14 As shown, in some embodiments, the side of the wind impeller outer edge 64 facing the blade 61 may further have a reinforcing portion 641 to strengthen the strength of the wind impeller outer edge 64 through the reinforcing portion 641, further improve the strength of the wind impeller 60, avoid the deformation of the wind impeller 60 at a higher temperature, and ensure the structural stability of the wind impeller 60.

[0172] Refer to Figure 14 As shown, in some embodiments, the surface of the reinforcing portion 641 facing the blade 61 may have a concave surface 6411. A part of the blade 61 may be located within the concave surface 6411 and be in contact with the concave surface 6411. Or, in some embodiments, the surface of the reinforcing portion 641 facing the blade 61 may not be provided with a concave surface 6411, that is, the surface of the reinforcing portion 641 facing the blade 61 may also be a flat surface.

[0173] Compared with the flat surface design of the surface of the reinforcing portion 641 facing the blade 61, when the surface of the reinforcing portion 641 facing the blade 61 is a concave surface 6411, while strengthening the strength of the wind impeller outer edge 64 through the reinforcing portion 641, the thickness reduction of the wind impeller outer edge 64 can also be achieved. And, through the setting of the concave surface 6411, the influence of the existence of the reinforcing portion 641 on the flow rate of the air flow generated by the wind impeller 60 can be minimized.

[0174] Taking the surface of the reinforcing portion 641 facing the blade 61 as a concave surface 6411 as an example, the structure of the wind impeller 60 will be further elaborated below.

[0175] See Figure 14 As shown, the reinforcing part 641 can be an annular structure, so that the reinforcing part 641 is provided on one side of the outer edge 64 of the wind impeller facing the blade 61. In some embodiments, the cross-sectional shape of the outer edge 64 of the wind impeller at the reinforcing part 641 can be a "U" - shaped structure or other shapes. Through experimental verification, when the reinforcing part 641 is an annular structure and the cross-sectional shape of the outer edge 64 of the wind impeller at the reinforcing part 641 is a "U" - shaped structure, while minimizing the influence of the existence of the reinforcing part 641 on the flow rate of the air flow generated by the wind impeller 60, it can also reduce the wind noise.

[0176] It should be noted that the brief description of the terms in this application is only for the convenience of understanding the following described embodiments, rather than intending to limit the embodiments of this application. Unless otherwise specified, these terms should be understood in their ordinary and common meanings.

[0177] Figure 15 Shows Figure 12 An enlarged view at C.

[0178] See Figure 15 As shown, in some embodiments, the blade 61 can be an arc - shaped structure, and a horizontal section 611 can be further provided on the side of the blade 61 away from the wind impeller chassis 63. Through the setting of the horizontal section 611, it can also guide the air flow flowing out from two adjacent air ducts 62, so that the air flow can flow along the horizontal section 611 towards the side of the air outlet of the volute 41. At the same time, it can also reduce the wind noise.

[0179] It should be noted that the dryer mentioned above in the embodiments of this application can be defined as the first type of dryer.

[0180] Based on the simulation analysis of the cooperation between the wind impeller and the volute of the dryer in the related technology above, the embodiments of this application also provide another dryer 100. Among them, the other dryer 100 can be defined as the second type of dryer. The difference from the first type of dryer is that in the second type of dryer provided by the embodiments of this application, the gap between the wind impeller 60 and the volute 41 is optimized. When the setting of the wind impeller 60 in the volute 41 is the same as that of the traditional dryer, the dryer 100 of the embodiments of this application can reduce the gap between the wind impeller 60 and the volute 41 along the radial direction of the wind impeller 60, which can greatly reduce the overall machine wind noise, and at the same time can reduce the overall machine power, thereby reducing the overall machine power consumption and improving the energy efficiency of the dryer 100.

[0181] It should be noted that for the structure and relative positions of the housing, cylinder, base, motor, air guide plate, wind impeller, evaporator and condenser in the second type of dryer, reference can be made to the relevant descriptions in the first type of dryer, which will not be elaborated here.

[0182] The following mainly combines with the attached drawings to further elaborate on the differences between the second clothes dryer and the first clothes dryer.

[0183] See Figure 3 As shown, when at least part of the impeller 60 is disposed in the accommodating cavity, in the radial direction of the impeller 60, the minimum distance L between the impeller 60 and the transition section 4121 is greater than or equal to 0.07 times the outer diameter D1 of the impeller 60 and less than or equal to 0.09 times the outer diameter D1 of the impeller 60. That is to say, the minimum distance L between the impeller 60 and the transition section 4121 takes a value between 0.07 times and 0.09 times the outer diameter D1 of the impeller 60. For example, the minimum distance L between the impeller 60 and the transition section 4121 can be 0.07 times, 0.075 times, 0.08 times, 0.085 times or 0.09 times the outer diameter D1 of the impeller, etc.

[0184] Compared with other parts of the volute tongue 412, the transition section 4121 is closer to the impeller 60. The gap between the impeller 60 and the transition section 4121 has a certain impact on the efficiency and wind noise of the impeller 60.

[0185] If, in the radial direction of the impeller 60, the minimum distance L between the impeller 60 and the transition section 4121 is too close (less than 0.07 times the outer diameter D1 of the impeller 60), it will cause the air flow generated by the impeller 60 to be difficult to be ejected from the tangent direction and flow to the air outlet end of the volute 41, and eddy currents will be generated in the transition section 4121, resulting in energy loss, which will cause the efficiency of the impeller 60 to decrease. Moreover, since the air flow is difficult to be ejected and flow to the air outlet end of the volute 41, the wind noise generated by the impeller 60 at the position where the distance from the transition section 4121 or the spiral section 4111 is small will increase locally.

[0186] If, in the radial direction of the impeller 60, the minimum distance L between the impeller 60 and the transition section 4121 is infinitely large (greater than 0.09 times the outer diameter D1 of the impeller 60), although the above-mentioned problem of local increase in wind noise can be improved, it will cause the guiding effect of the volute 41 on the air flow generated by the impeller 60 to be very weak, and the air flow generated by the impeller 60 will disperse everywhere, and it is difficult to be guided out of the air outlet end along the spiral section 4111 from the position where the volute tongue 412 is located, which will also cause the efficiency of the impeller 60 to decrease.

[0187] Therefore, when the minimum distance L between the wind impeller 60 and the transition section 4121 in the embodiments of the present application is set between 0.07 times and 0.09 times the outer diameter D1 of the wind impeller 60, the minimum distance L between the wind impeller 60 and the transition section 4121 can be controlled within a more appropriate range, which can prevent the airflow generated by the wind impeller 60 from generating eddy currents in the transition section 4121, ensure that the wind impeller 60 has higher efficiency, and at the same time avoid local increase in wind noise. When ensuring that the effective air volume output by the wind impeller 60 remains unchanged, due to the higher efficiency of the wind impeller 60, the work done by the motor to drive the wind impeller 60 will be less, the power consumption will be smaller, and it will be more energy-efficient. The power of the motor can be appropriately reduced, and the power and power consumption of the whole machine are both reduced, so that a better balance can be achieved among the drying speed, power consumption, and wind noise of the dryer 100. When the power of the whole machine is reduced and the wind noise is reduced, the energy efficiency of the dryer 100 can be improved.

[0188] Refer to Figure 3 As shown, in some embodiments, the side where the transition section 4121 is connected to the other end of the spiral section 4111 can be defined as the connection side 4123, and the connection side 4123 is located on the side of the transition section 4121 facing the wind impeller 60.

[0189] In the radial direction of the wind impeller 60: the distance between the wind impeller 60 and the connection side 4123 is less than the distance between the wind impeller 60 and the rest of the transition section 4121, and the distance between the wind impeller 60 and the connection side 4123 is also less than the distance between the wind impeller 60 and the spiral section 4111. That is to say, in the radial direction of the wind impeller 60, the distance between the wind impeller 60 and the connection side 4123 is the minimum distance between the wind impeller 60 and the transition section 4121 and the spiral section 4111. This distance is equal to the above minimum distance L, that is, the distance between the wind impeller 60 and the connection side 4123 can be set between 0.07 times and 0.09 times the outer diameter D1 of the wind impeller 60.

[0190] In addition to the transition section 4121, the end of the spiral section 4111 connected to the transition section 4121 is also relatively close to the wind impeller 60. The gap between the wind impeller 60 and the spiral section 4111 also has a certain impact on the efficiency and wind noise of the wind impeller 60.

[0191] When the distance between the wind impeller 60 and the connection side 4123 in the embodiments of the present application can be set between 0.07 times and 0.09 times the outer diameter D1 of the wind impeller 60, the minimum distance between the wind impeller 60 and the spiral section 4111 can be controlled within a more appropriate range, avoiding the influence of the too-close distance between the spiral section 4111 and the wind impeller 60 on the efficiency and wind noise of the wind impeller 60, and further avoiding local increase in wind noise, so that the efficiency of the wind impeller 60 can be further improved.

[0192] For the second dryer, when the setting of the impeller 60 in the volute 41 is the same as that of the conventional dryer, to ensure that the minimum distance L between the impeller 60 and the transition section 4121 is between 0.07 times and 0.09 times the outer diameter D1 of the impeller 60, the present application also adjusts and optimizes the parameters of the impeller 60. Without affecting the drying speed, it can greatly reduce the overall wind noise of the whole machine, and at the same time can reduce the overall power of the whole machine, thereby reducing the overall power consumption and improving the energy efficiency of the dryer 100, so that a better balance can be achieved among the drying speed, power consumption and wind noise of the dryer 100.

[0193] The following further elaborates on the parameters of the impeller 60 of the present application in conjunction with the drawings and embodiments.

[0194] See Figure 9 As shown, in the second dryer provided by the embodiment of the present application, the outer diameter D1 of the impeller 60 can also be greater than or equal to 130 mm and less than or equal to 140 mm, that is, the outer diameter D1 of the impeller 60 can be between 130 - 140 mm. Examples of the number of values of the outer diameter D1 of the impeller 60 can refer to the relevant description in the first dryer and will not be elaborated here.

[0195] Compared with the outer diameter of the impeller in the related technology mentioned above being between 155 - 160 mm, in the second dryer provided by the embodiment of the present application, by limiting the size of the outer diameter D1 of the dryer 100, the outer diameter of the impeller 60 can be reduced, so that the overall size of the impeller 60 is reduced. In this way, when the installation position of the impeller 60 in the volute 41 and the size of the volute 41 remain unchanged, the gap between the impeller 60 and the volute 41 can be increased. In particular, the gap between the impeller 60 and the volute tongue 412 of the volute 41 at the end facing the impeller 60 (transition section 4121) can be increased. Specifically, when the installation position of the impeller 60 in the volute 41 and the size of the volute 41 remain unchanged, the distance L between the impeller 60 and the connecting edge 4123 can be between 0.07 times and 0.09 times the outer diameter D1 of the impeller 60. For example, when the outer diameter D1 is 132 mm, the distance L between the impeller 60 and the connecting edge 4123 can be greater than or equal to 9 mm and less than or equal to 12 mm.

[0196] When the distance L between the wind impeller 60 and the connecting edge 4123 is within the range of 0.07 times to 0.09 times the outer diameter D1 of the wind impeller 60, it can effectively avoid the occurrence of eddy currents in the transition section 4121 of the air flow generated by the wind impeller 60. As a result, when the air flow generated by the wind impeller 60 passes through the transition section 4121, there will be no significant speed change, ensuring the smoothness of the air flow. This can prevent the energy loss caused by the eddy current flowing back into the wind impeller 60 when the air flow passes through the end of the volute tongue 412 facing the wind impeller 60, and the efficiency of the wind impeller 60 is improved. In this way, while ensuring that the effective air volume output of the wind impeller 60 remains unchanged, the motor needs to do less work to drive the wind impeller 60, consuming less power, being more energy-efficient, the power of the motor can be reduced, and the power and power consumption of the whole machine are both reduced.

[0197] Moreover, since the occurrence of eddy currents in the transition section 4121 of the air flow generated by the wind impeller 60 is avoided, the air flow generated by the wind impeller 60 can normally enter the cylinder 10 through the air outlet end when passing through the transition section 4121, and will not circle locally in the transition section 4121 of the volute tongue 412. Therefore, the wind noise is greatly reduced. Therefore, when the power of the whole machine is reduced and the wind noise is reduced, the energy efficiency of the dryer 100 can be improved.

[0198] See Figure 9 As shown, in some embodiments, when the outer diameter D1 of the wind impeller 60 is greater than or equal to 130 mm and less than or equal to 140 mm, the inner diameter D2 of the wind impeller 60 can also be greater than or equal to 100 mm and less than or equal to 110 mm. That is to say, the inner diameter D2 of the wind impeller 60 can take values between 100 - 110 mm. For examples of the value points of the inner diameter D2 of the wind impeller 60, reference can be made to the relevant description in the first dryer, which will not be elaborated here.

[0199] Since the inner diameter D2 of the wind impeller 60 determines the air intake volume of the wind impeller 60.

[0200] When the outer diameter D1 of the wind impeller 60 is greater than or equal to 130 mm and less than or equal to 140 mm, if the inner diameter D2 of the wind impeller 60 is too large (greater than 140 mm), the air intake volume of the wind impeller 60 increases. At the same time, along the radial direction of the wind impeller 60, the size of the blades 61 in the wind impeller 60 decreases (the blades 61 become narrower). The blades 61 are always stirring the air, making it difficult for the air in the wind impeller 60 to be thrown out between adjacent blades 61, resulting in a decrease in the air flow rate (air volume) of the air flow generated by the wind impeller 60, and large wind noise will also be generated.

[0201] When the outer diameter D1 of the wind impeller 60 is greater than or equal to 130 mm and less than or equal to 140 mm, if the inner diameter D2 of the wind impeller 60 is on the small side (less than 130 mm), the air intake of the wind impeller 60 will decrease, which may lead to insufficient air intake of the wind impeller 60 and affect the drying speed.

[0202] Compared with the wind impeller with an outer diameter between 155 - 160 mm in the related art, when the outer diameter D1 of the wind impeller 60 in the embodiment of the present application is greater than or equal to 130 mm and less than or equal to 140 mm, when the inner diameter D2 of the wind impeller 60 takes a value between 100 - 110 mm, while ensuring the air intake of the wind impeller 60, so that the inner diameter D2 of the wind impeller 60 cooperates with the outer diameter D1, the wind impeller 60 can generate a larger air flow rate, without affecting the drying speed, while reducing the wind noise.

[0203] Therefore, by limiting the values of the outer diameter D1 and the inner diameter D2 of the wind impeller 60, after ensuring that the size of the wind impeller 60 is reduced, compared with the wind impeller 60 with a large outer diameter in the related art, without affecting the drying speed, it can greatly reduce the wind noise, improve the efficiency of the wind impeller 60, reduce the power and power consumption of the whole machine, make the dryer 100 more energy-saving, improve the energy efficiency, and enable a better balance among the drying speed, power consumption and wind noise of the dryer 100.

[0204] Same as the first dryer, through experimental verification, compared with the dryer using a wind impeller with an outer diameter between 155 - 160 mm mentioned above, after optimizing the outer diameter D1 and the inner diameter D2 of the wind impeller 60 in the second dryer provided by the embodiment of the present application, the overall power of the dryer 100 is reduced by at least 15 w, making the dryer 100 more power-saving. At the same time, the wind noise of the dryer 100 is reduced by at least 3 dB, greatly improving the user experience.

[0205] It should be noted that the descriptions of the air intake and outlet modes of the wind impeller 60, the arrangement of the blades 61, the formation of the air duct 62, the value of the outlet angle β1 of the blades 61, etc. are the same as the relevant descriptions in the first dryer, and will not be repeated here. See Figure 11 As shown, when the sizes of the outer diameter D1 and the inner diameter D2 of the wind impeller 60 are determined, the approximate range of the air flow rate (air volume) that the wind impeller 60 can generate has been basically determined. However, the outlet angle β1 of the blade 61 will also affect the air flow rate generated by the wind impeller 60.

[0206] For example, when the outer diameter D1 of the wind impeller 60 ranges from 130 mm to 140 mm and the inner diameter D2 of the wind impeller 60 ranges from 100 to 110 mm, if the outlet angle β1 of the blade 61 is too large (greater than 160°), the flow rate of the air flow generated by the wind impeller 60 will increase. However, the efficiency of the wind impeller 60 will decrease and the generated wind noise will increase.

[0207] For another example, when the outer diameter D1 of the wind impeller 60 ranges from 130 mm to 140 mm and the inner diameter D2 of the wind impeller 60 ranges from 100 to 110 mm, if the outlet angle β1 of the blade 61 is too small (greater than 150°), the flow rate of the air flow generated by the wind impeller 60 will decrease, and the air flow rate will be insufficient, affecting the drying speed and drying effect.

[0208] Therefore, when the outer diameter D1 and the inner diameter D2 of the wind impeller 60 in the second clothes dryer provided by the embodiments of the present application are within the above ranges, and the outlet angle β1 of each blade 61 can be within the range of 150° - 160°, the outlet angle β1 of each blade 61 can be controlled within a more appropriate range, and has a good matching degree with the outer diameter D1 and the inner diameter D2 of the impeller, so that the air duct 62 defined by adjacent blades 61 has a good air outlet effect. This can ensure that the wind impeller 60 can generate a large air flow rate, improve the efficiency of the wind impeller 60, so that after the outer diameter D1 of the wind impeller 60 is reduced, it will not affect the drying speed, and at the same time, it can avoid the generation of wind noise due to the too large outlet angle β1, so that a better balance can be achieved among the drying speed, power consumption and wind noise of the clothes dryer 100.

[0209] See Figure 11 As shown, in some embodiments, in the second clothes dryer provided by the embodiments of the present application, the inlet angle β2 of each blade 61 can also be greater than or equal to 55° and less than or equal to 65°, that is, the inlet angle β2 of each blade 61 can be within the range of 55° - 65°. The example of the value points of the inlet angle β1 of the wind impeller 60 and the definition of the inlet angle β2 can also be referred to the relevant description in the first clothes dryer, which will not be elaborated here.

[0210] It should be noted that

[0211] When the outer diameter D1 of the wind impeller 60 ranges between 130 mm and 140 mm, the inner diameter D2 of the wind impeller 60 ranges between 100 - 110 mm, the outlet angle β1 of the blade 61 ranges between 150° - 160°, and the inlet angle β2 of the blade 61 ranges between 55° - 65°, it can make the shape of the blade 61 adapt to the dimensions of the outer diameter D1 and the inner diameter D2 of the wind impeller 60, so that the air duct 62 defined by adjacent blades 61 has better air inlet and outlet effects, ensuring that the wind impeller 60 can generate a larger air flow rate, further improving the efficiency of the wind impeller 60, so that after the outer diameter D1 of the wind impeller 60 is reduced, it will not affect the drying speed of the wind impeller 60, and further enhancing the balance among the drying speed, power consumption, and wind noise of the dryer 100.

[0212] See Figure 11 As shown, in some embodiments, when the outer diameter D1 of the wind impeller 60 ranges between 130 mm and 140 mm and the inner diameter D2 of the wind impeller 60 ranges between 100 - 110 mm, the number of blades 61 can be greater than or equal to 33 and less than or equal to 39, that is, the number of blades 61 can range between 33 and 39. For example, the example of the value points of the blade 61 can refer to the relevant description in the first dryer and will not be elaborated here.

[0213] When designing the wind impeller 60, the number of blades 61 generally matches the diameter of the wind impeller 60 (such as the outer diameter D1 and the inner diameter D2). For example, when the outer diameter D1 of the wind impeller 60 ranges between 130 mm and 140 mm and the inner diameter D2 of the wind impeller 60 ranges between 100 - 110 mm, if the number of blades 61 is too large (more than 39), the arrangement of the blades 61 in the wind impeller 60 is relatively dense, and when air flows through the air duct 62 between adjacent blades 61, wind noise is likely to be generated; if the number of blades 61 is too small (less than 33), the arrangement of the blades 61 in the wind impeller 60 is relatively sparse, easily causing the air flow generated by the wind impeller 60 in the air duct 62 between adjacent blades 61 to be unstable, with the air flow being sometimes large and sometimes small.

[0214] When the outer diameter D1 of the wind impeller 60 ranges between 130 mm and 140 mm, the inner diameter D2 of the wind impeller 60 ranges between 100 - 110 mm, and the number of blades 61 ranges between 33 - 39, it can control the number of blades 61 within a more appropriate range, making the number of blades 61 match the diameter of the wind impeller 60, further reducing the wind noise generated by the wind impeller 60, and further enhancing the balance among the drying speed, power consumption, and wind noise of the dryer 100.

[0215] See Figure 12 and Figure 13As shown, in some embodiments, for the second clothes dryer, the impeller 60 may also include an impeller chassis 63, an impeller outer edge 64, and an air duct 62. The connection of the impeller chassis 63 in the clothes dryer, the setting positions of the impeller outer edge 64 and the impeller chassis 63 may be the same as the relevant descriptions in the first clothes dryer, and will not be elaborated here.

[0216] In some embodiments, the air duct 62 of the impeller 60 in the second clothes dryer may also communicate with the inlet 65 in the axial direction, so that after the air enters from the inlet 65, it can enter the air duct 62 to achieve axial air intake of the impeller 60. The diameter D3 of the inlet 65 may also be greater than or equal to 110 mm and less than or equal to 115 mm, that is, the diameter D3 of the inlet 65 may take values between 110 - 115 mm. For the example of the number of value points of the diameter D3 of the inlet 65, reference may also be made to the relevant descriptions in the first clothes dryer, and will not be elaborated here.

[0217] It should be understood that the diameter D3 of the inlet 65 determines the air intake volume of the impeller 60 and the structural strength of the impeller 60. For example, when the outer diameter D1 of the impeller 60 takes values between 130 mm and 140 mm, if the diameter D3 of the inlet 65 is too small (less than 110 mm), the inlet 65 decreases, the air intake volume decreases, and the airflow generated by the impeller 60 also decreases; if the diameter D3 of the inlet 65 is too large (greater than 115 mm), the inlet 65 increases, the air intake volume increases, and the airflow generated by the impeller 60 also increases, but the strength of the impeller 60 will become weaker. The closer the diameter D3 of the inlet 65 is to the outer diameter D1, the weaker the strength of the impeller 60. Since the air entering the impeller 60 in the clothes dryer 100 is hot air with a relatively high temperature, if the strength of the impeller 60 is relatively weak, the impeller 60 may be deformed at a relatively high temperature, affecting the structural stability of the impeller 60.

[0218] Therefore, compared with the impeller in the related technology mentioned above, when the outer diameter D1 takes values between 130 mm and 140 mm and the diameter D3 of the inlet 65 takes values between 110 - 115 mm, the impeller 60 has a relatively large air intake volume to ensure that the flow rate of the airflow generated by the impeller 60 is basically not affected. While further enhancing the balance among the drying speed, power consumption, and wind noise of the clothes dryer 100, it can also avoid having too much impact on the strength of the impeller 60, so that the structure of the impeller 60 is relatively stable and not easily deformed at a relatively high temperature.

[0219] In some embodiments, the formation position of the outlet 66 of the impeller 60 in the second clothes dryer, the diameter D4 of the impeller chassis 63, and the relationship between the diameter D4 of the impeller chassis 63 and the diameter D3 of the inlet 65 are the same as the relevant descriptions in the first clothes dryer, and will not be elaborated here.

[0220] See Figure 10 As shown, in some embodiments, the axial thickness b of the impeller 60 in the second clothes dryer may also be greater than or equal to 40 mm and less than or equal to 45 mm, that is, the axial thickness b of the impeller 60 may take values between 40-45 mm. For the example of the number of values of the axial thickness b of the impeller 60 and the thickness referred to, reference may also be made to the relevant description in the first clothes dryer, which will not be elaborated here.

[0221] The axial thickness b of the impeller 60 affects the flow rate of the air flow generated by the impeller 60. When the outer diameter D1 of the impeller 60 takes values between 130 mm and 140 mm and the inner diameter D2 of the impeller 60 takes values between 100-110 mm, if the axial thickness b of the impeller 60 is too large (greater than 45 mm), it is difficult for air to enter the impeller 60, and the strength of the impeller 60 is weakened and unstable; if the axial thickness b of the impeller 60 is too small (less than 40 mm), the inlet 65 of the impeller 60 is very large, but the outlet 66 is very small. Air can enter the impeller 60, but it is difficult to be thrown out.

[0222] When the outer diameter D1 of the impeller 60 takes values between 130 mm and 140 mm, the inner diameter D2 of the impeller 60 takes values between 100-110 mm, and the axial thickness b of the impeller 60 takes values between 40-45 mm, the axial thickness b of the impeller 60 can be controlled within a more appropriate range, so that the axial thickness b of the impeller 60 matches the diameter (inner diameter D2 and outer diameter D1) of the impeller 60, so as to avoid the axial thickness b of the impeller 60 affecting the flow rate of the air flow generated by the impeller 60, and can further enhance the balance among the drying speed, power consumption and wind noise of the clothes dryer 100. At the same time, it can also avoid the weakening of the strength of the impeller 60.

[0223] See Figure 14 As shown, in some embodiments, for the second clothes dryer, the outer edge 64 of the impeller may also have a reinforcing portion 641 to further enhance the strength of the impeller 60, avoid the impeller 60 from deforming at a higher temperature, and ensure the structural stability of the impeller 60.

[0224] See Figure 14As shown, in some embodiments, in the second type of clothes dryer, the side of the reinforcement part 641 facing the blade 61 may also have a recessed surface 6411. Part of the blade 61 may be located in the recessed surface 6411 and connected to the recessed surface 6411. Compared with the planar design of the side of the reinforcement part 641 facing the blade 61, when the side of the reinforcement part 641 facing the blade 61 is the recessed surface 6411, while the strength of the outer edge 64 of the wind impeller is strengthened by the reinforcement part 641, the outer edge 64 of the wind impeller can also be thinned, and the presence of the reinforcement part 641 can also minimize the influence of the flow rate of the airflow generated by the wind impeller 60.

[0225] The structure of the second type of impeller 60 for the clothes dryer is further described below by taking the side of the reinforcement portion 641 facing the blade 61 as the concave surface 6411 as an example.

[0226] See also Figure 14 As shown, for the second type of clothes dryer, in some embodiments, the reinforcement part 641 can be an annular structure, so that the side of the outer edge 64 of the wind impeller facing the blade 61 is provided with the reinforcement part 641. In some embodiments, the recessed surface 6411 includes a bottom wall 6412 and two side walls 6413. The two side walls 6413 are symmetrically arranged on both sides of the bottom wall 6412. For example, one side wall 6413 is arranged on the side of the bottom wall 6412 facing the wind impeller chassis 63, and the other side wall 6413 is symmetrically arranged on the side of the bottom wall 6412 away from the wind impeller chassis 63. Both side walls 6413 are connected to the bottom wall 6412, and together with the bottom wall 6412, they form an annular groove 6414. Part of the blade 61 is arranged in the annular groove 6414 and connected to the bottom wall 6412, so that part of the blade 61 can be located in the recessed surface 6411 and connected to the recessed surface 6411.

[0227] See also Figure 14 As shown, since the bottom wall 6412 of the recessed surface 6411 and the two side walls 6413 together form an annular groove 6414, the cross-section of the outer edge 64 of the wind impeller at the reinforcement portion 641 can be a "U"-shaped structure, or other structures similar to the "U"-shaped structure with two side walls 6413 symmetrical.

[0228] It should be noted that when the two side walls 6413 on both sides of the bottom wall 6412 are of an asymmetric structure, the cross-section of the outer edge 64 of the wind impeller at the reinforcement portion 641 may also be of other shapes.

[0229] After a large number of experimental verifications, compared with the two side walls 6413 on both sides of the bottom wall 6412 being asymmetric structures, when the reinforcing part 641 is an annular structure, and the outer edge 64 of the wind impeller has a "U" - shaped cross - section in the reinforcing part 641 or other structures symmetric to the two side walls 6413 similar to the "U" - shaped structure, while minimizing the impact of the existence of the reinforcing part 641 on the flow rate of the air flow generated by the wind impeller 60, the wind noise can also be reduced.

[0230] See Figure 15 As shown, for the second type of dryer, in some embodiments, the blade 61 can be an arc - shaped structure, and a horizontal cutting surface 611 can also be provided on the side of the blade 61 away from the wind impeller chassis 63, so that the air flow can flow along the horizontal cutting surface 611 towards the side of the air outlet of the volute 41. At the same time, the wind noise can also be reduced.

[0231] In addition, the terms "comprising" and "having" and any variations thereof are intended to cover but not exclude inclusion. For example, a product or device comprising a series of components does not necessarily have to be limited to those components clearly listed, but may include other components not clearly listed or inherent to these products or devices.

[0232] In the description of the present application, it should be understood that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation to the present application.

[0233] The terms "first" and "second" are only used for descriptive purposes and cannot be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present application, unless otherwise stated, the meaning of "a plurality" is two or more.

[0234] In the description of the present application, it should be noted that unless otherwise clearly specified and defined, the terms "installed", "connected", and "coupled" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific circumstances.

[0235] Next, the technical solutions in the embodiments of the present application will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present application.

[0236] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present application, rather than to limit them; although the present application has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that they can still modify the technical solutions described in the foregoing embodiments, or equivalently replace some or all of the technical features; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the scope of the technical solutions of the embodiments of the present application.

[0237] For the sake of convenience of explanation, the above description has been made in conjunction with specific embodiments. However, the above exemplary discussions are not intended to be exhaustive or to limit the embodiments to the specific forms disclosed above. According to the above teachings, various modifications and variations can be obtained. The selection and description of the above embodiments are for the purpose of better explaining the principles and practical applications, so that those skilled in the art can better use the embodiments and various different variations of the embodiments suitable for specific use considerations.

Claims

1. A clothes dryer, characterized in that, Comprising: A housing; A cylinder body, rotatably arranged inside the housing; A base, arranged inside the housing, and the cylinder body is arranged on one side of the base facing the top of the housing; A motor, arranged inside the base and connected to the cylinder body, and the motor is configured to be able to drive the cylinder body to rotate relative to the housing; A wind guide plate, installed outside the housing, and a volute is provided inside the wind guide plate, and the volute is communicated with the inside of the cylinder body; A wind impeller, at least part of the wind impeller is arranged inside the volute and communicated with the inside of the base; the wind impeller is connected to the motor and rotates under the drive of the motor to generate an air flow; Wherein, the volute is configured to be able to guide the air flow generated by the wind impeller into the cylinder body to heat the object to be dried inside the cylinder body; An evaporator and a condenser, both located inside the base, the evaporator is configured to be able to condense the flowing air flow when the air flow heats the object to be dried and enters the base, so that the air flow precipitates moisture; the condenser is configured to heat the condensed air flow, and the air flow heated by the condenser can enter the cylinder body again through the wind impeller and the volute; Wherein, the outer diameter of the wind impeller is greater than 130 mm and less than 140 mm, and the inner diameter of the wind impeller is greater than 100 mm and less than 110 mm.

2. A dryer, characterized in that, Comprising: A housing; A cylinder body, rotatably arranged inside the housing; A base, arranged inside the housing, and the cylinder body is arranged on one side of the base facing the top of the housing; A motor, arranged inside the base and connected to the cylinder body, and the motor is configured to be able to drive the cylinder body to rotate relative to the housing; A wind guide plate, installed outside the housing, and a volute is provided inside the wind guide plate, and the volute is communicated with the inside of the cylinder body; The volute includes: A volute body, the volute body includes a spiral section and an extension section, the spiral section defines a receiving cavity, and one end of the spiral section is connected to the extension section; A volute tongue, the volute tongue includes a transition section and a diffusion section, the transition section is arc-shaped, the other end of the spiral section is connected to one end of the transition section, the other end of the transition section is connected to the diffusion section, and the diffusion section and the extension section define the air outlet end of the volute; A wind impeller, at least part of the wind impeller is arranged inside the receiving cavity, and along the radial direction of the wind impeller, the minimum distance between the wind impeller and the transition section is greater than 0.07 times the outer diameter of the wind impeller and less than 0.09 times the outer diameter of the wind impeller; The wind impeller is communicated with the inside of the base; The wind impeller is connected to the motor and rotates under the drive of the motor to generate an air flow, and the air flow flows out from the air outlet end and enters the cylinder body to heat the object to be dried inside the cylinder body; An evaporator and a condenser, both located inside the base, the evaporator is configured to be able to condense the flowing air flow when the air flow heats the object to be dried and enters the base, so that the air flow precipitates moisture; The condenser is configured to heat the air stream to be condensed, and the air stream heated by the condenser can enter the cylinder body again via the wind impeller and the volute.

3. The dryer according to claim 2, wherein Define the side where the transition section is connected to the other end of the spiral section as the connection side, and the connection side is located on the side of the transition section facing the wind impeller; In the radial direction of the wind impeller: the distance between the wind impeller and the connection side is less than the distance between the wind impeller and the rest of the transition section, and the distance between the wind impeller and the connection side is also less than the distance between the wind impeller and the spiral section.

4. The dryer according to claim 3, wherein, The outer diameter of the wind impeller is greater than or equal to 130 mm and less than or equal to 140 mm, and the inner diameter of the wind impeller is greater than 100 mm and less than 110 mm.

5. The dryer according to claim 1 or 4, characterized in that, The wind impeller includes: A plurality of blades, arranged at intervals in the circumferential direction of the wind impeller; The outlet angle of each blade is greater than 150° and less than 160°.

6. The dryer according to claim 5, characterized in that, The inlet angle of each blade is greater than 55° and less than 65°.

7. The dryer according to claim 5, characterized in that, The number of the blades is greater than 33 and less than 39.

8. The dryer according to claim 5, characterized in that, The wind impeller includes: A wind impeller chassis, configured to be connected to the motor; A wind impeller outer edge, spaced apart from the wind impeller chassis in the axial direction of the wind impeller; The plurality of blades are arranged at intervals in the circumferential direction of the wind impeller chassis, and in the axial direction of the wind impeller, one end of each blade is connected to the wind impeller chassis and the other end is connected to the wind impeller outer edge.

9. The dryer according to claim 8, characterized in that, The wind impeller has an outlet, and the outlet is formed on the circumferential side of the wind impeller chassis, and the diameter of the wind impeller chassis constitutes the inner diameter of the outlet; The diameter of the wind impeller chassis is greater than 108 mm and less than 115 mm.

10. The dryer according to claim 8, characterized in that, One side of the wind impeller outer edge facing the blade further has a strengthening portion, and the surface of the strengthening portion facing the blade has a concave surface; A part of the blade is arranged in the concave surface and is connected to the concave surface.

11. The dryer according to claim 10, characterized in that, The strengthening portion is a ring structure, and the concave surface includes a bottom wall and two side walls. The two side walls are symmetrically arranged on both sides of the bottom wall, and both side walls are connected to the bottom wall and jointly enclose a ring groove with the bottom wall; A part of the blade is arranged in the ring groove and is connected to the bottom wall.

12. The dryer according to claim 5, characterized in that, The axial thickness of the wind impeller is greater than 40 mm and less than 45 mm.

13. The dryer according to claim 5, characterized in that, Each wind impeller has an inlet in the axial direction, and the diameter of the inlet is greater than 110 mm and less than 115 mm.

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