WO2019109476A1

WO2019109476A1 - Clothes dryer and cooling air inlet structure therefor

Info

Publication number: WO2019109476A1
Application number: PCT/CN2018/073088
Authority: WO
Inventors: 周胜利; 马娜娜; 顾超林; 梅红杰
Original assignee: 无锡小天鹅股份有限公司
Priority date: 2017-12-08
Filing date: 2018-01-17
Publication date: 2019-06-13

Abstract

A clothes dryer (1) and a cooling air inlet structure (30) therefor. The cooling air inlet structure (30) for the clothes dryer (1) comprises a housing (100) and an air inlet pipe (200). The air inlet pipe (200) passes through the housing (100). An air inlet channel (210) is defined in the air inlet pipe (200), and the housing (100) and the peripheral wall surface of the air inlet pipe (200) together define an expansion chamber (110). The peripheral wall of the air inlet pipe (200) is provided with multiple through holes (220) making the air inlet channel (210) in communication with the expansion chamber (110). The cooling air inlet structure (30) for the clothes dryer (1) can reduce the wind noise of cooling air, thus reducing the noise of the whole machine.

Description

Dryer and cooling air inlet structure

Technical field

The present invention relates to the field of electrical appliance manufacturing technology, and in particular to a cooling air inlet structure for a clothes dryer and a clothes dryer having the cooling air inlet structure for a clothes dryer.

Background technique

In the related art, a dryer such as a condensing type has a small structural noise in its overall noise configuration, and wind noise is a main component.

For the condensing dryer, the cooling air volume and the circulating air volume are roughly the same, and both use a centrifugal fan, so the wind noise of the cooling wind is substantially the same as the circulating wind noise only from the noise source. However, the circulating wind flows in the body. When the noise propagates outward, it needs to pass through the tube, the air passage, the base, and the layer of the box is blocked. The cooling air inlet channel is directly exposed to the air, and the wind noise of the cooling wind can be without any Blocking enters the outside world, so in the noise of the dryer, the noise generated by the cooling wind is the main noise.

Since the wind noise belongs to the middle and low frequency noise, the sound absorbing material such as the sound absorbing cotton can have a limited noise reduction effect, and at the same time, in order to ensure the smoothness of the air inlet, the cooling air inlet passage cannot be sealed and soundproofed, so the dryer cools the air passage. The noise reduction design has always been a major difficulty.

Summary of the invention

The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a cooling air inlet structure for a clothes dryer, and the cooling air inlet structure for the dryer can reduce the wind noise of the cooling wind, thereby reducing the noise of the whole machine. .

The present invention also provides a dryer having the cooling air inlet structure for a clothes dryer.

According to an embodiment of the first aspect of the present invention, a cooling air intake structure for a clothes dryer is provided, the cooling air intake structure for a clothes dryer comprising: an outer casing; an air inlet pipe, the inlet a duct passing through the outer casing, the air inlet duct defines an air inlet passage, and the outer casing and the outer peripheral wall surface of the air inlet duct jointly define an expansion chamber, and the peripheral wall of the air inlet duct is connected The air inlet passage and the plurality of perforations of the expansion chamber.

According to an embodiment of the second aspect of the present invention, a cooling air inlet structure for a clothes dryer is provided, the cooling air intake structure for a clothes dryer comprising: an air inlet duct, the air inlet duct defining An air inlet duct; the outer casing shell is disposed on the air inlet duct; the outer casing shell and the outer peripheral wall surface of the air inlet duct jointly define an expansion chamber, and the peripheral wall of the air inlet duct is disposed There are a plurality of perforations connecting the inlet passage and the expansion chamber, each of the perforations having a cross-sectional area greater than or equal to 19.6 mm ² .

According to an embodiment of the third aspect of the present invention, a cooling air intake structure for a clothes dryer is provided, the cooling air intake structure for a clothes dryer comprising: an air inlet duct, the air inlet duct defining An air inlet duct; the outer casing shell is disposed on the air inlet duct; the outer casing shell and the outer peripheral wall surface of the air inlet duct jointly define an expansion chamber, and the peripheral wall of the air inlet duct is disposed There are a plurality of perforations connecting the inlet passage and the expansion chamber, the perforations being circular holes having a diameter greater than or equal to 2.5 mm.

The cooling air inlet structure for a clothes dryer according to an embodiment of the present invention can reduce the wind noise of the cooling air, thereby achieving a noise reduction effect on the whole machine.

According to some embodiments of the invention, the air inlet duct passes through the outer casing.

According to some embodiments of the present invention, the outer casing includes: a casing including a peripheral wall and an end wall connected to one end of the peripheral wall, the peripheral wall being disposed around the inlet duct, the inlet a duct passing through the end wall, the end wall being adjacent to one end of the air inlet duct and sealingly connected to an outer peripheral wall surface of the air inlet duct; a sealing member, the air inlet duct passing through the sealing member The seal member is adjacent to the other end of the air inlet duct, and the seal member is sealingly connected to the outer peripheral wall surface of the air inlet duct and the other end of the peripheral wall, respectively.

Further, at least two of the housing, the seal and the air inlet tube are integrally formed.

According to some specific examples of the present invention, the perforations are arranged on the peripheral wall of the air inlet duct in a plurality of rows spaced along the axial direction of the air inlet duct and spaced apart in the circumferential direction of the air inlet duct. Column.

According to some embodiments of the invention, the air inlet duct has a plurality of sections arranged along its axial direction, wherein the perforation ratio of any two sections is different from the cross-sectional area of the perforations.

According to some embodiments of the present invention, further comprising a partition disposed in the expansion chamber and dividing the expansion chamber into a plurality of sub-chambers that communicate with the air inlet passage through the perforations, respectively .

According to some embodiments of the invention, at least two of the portions of the expansion chamber in the axial direction thereof have different cross-sectional areas.

Further, the cross-sectional area of the expansion chamber is tapered in its axial direction.

Further, a cross-sectional area of at least one of the air inlet duct and the outer casing is gradually changed in an axial direction thereof.

Further, the cross-sectional area of the expansion chamber is abrupt in its axial direction.

Further, a cross-sectional area of at least one of the air inlet duct and the outer casing is abrupt in its axial direction.

According to some embodiments of the invention, the air inlet ducts are a plurality of coaxially disposed.

According to some specific examples of the invention, each of the perforations has a cross-sectional area greater than or equal to 19.6 mm ² .

According to some specific examples of the invention, the perforations are circular holes having a diameter greater than or equal to 2.5 mm.

According to some specific examples of the invention, the inner diameter of the air inlet duct is 0.7 to 12.2 times the outer diameter of the outer circulation air guiding device.

According to some specific examples of the invention, the length of the air inlet duct along its axial direction is less than or equal to 200 mm.

According to some specific examples of the invention, the length of the air inlet duct along its axial direction is 90 to 150 mm.

According to some specific examples of the invention, the expansion chamber has a circular cross section, the outer diameter of the expansion chamber is less than or equal to 200 mm, and the depth of the expansion chamber along its axial direction is less than or equal to 250 mm.

According to some specific examples of the invention, the air inlet duct is a metal tube, and the air inlet duct has a wall thickness of 0.2 to 1.5 mm.

According to some specific examples of the invention, the air inlet duct is a plastic tube, and the air inlet duct has a wall thickness of 2 to 4 mm.

An embodiment according to a fourth aspect of the present invention provides a clothes dryer comprising a cooling air intake structure for a clothes dryer according to an embodiment of the first aspect of the present invention.

The clothes dryer according to the embodiment of the present invention has an advantage of being low in noise by utilizing the cooling air intake structure for the clothes dryer according to the embodiment of the first aspect of the present invention.

According to some embodiments of the invention, the dryer is a condensing dryer.

Further, the dryer comprises: a body having a dry clothes chamber; an inner circulation system, the inner circulation system being mounted to the body and including an inner circulation air guiding device and a heating device, the inner circulation The air guiding device is configured to circulate air in the drying chamber, and the circulating air is heated when flowing through the heating device, and the heated air evaporates the moisture of the clothes in the drying chamber. a humid air; an external circulation system, the outer circulation system being installed in the body and comprising the cooling air inlet structure, an outer circulation air guiding device and a condenser, wherein the outer circulation air guiding device is used for The air passage is guided by the air to the condenser to cool the condenser, the condenser is used to condense moisture in the moist hot air flowing therethrough into water droplets; the water tank is used, and the water tank is used for receiving a water droplet on the condenser; a driving device, wherein the driving device is respectively drivingly connected to the inner circulation air guiding device and the outer circulation air guiding device.

The additional aspects and advantages of the invention will be set forth in part in the description which follows.

DRAWINGS

The above and/or additional aspects and advantages of the present invention will become apparent and readily understood from

1 is a schematic structural view of a cooling air inlet structure for a clothes dryer according to an embodiment of the present invention.

2 is a cross-sectional view of a cooling wind inlet structure for a clothes dryer in accordance with an embodiment of the present invention.

3 is a cross-sectional view of a cooling air inlet structure for a clothes dryer in accordance with a first alternative embodiment of the present invention.

Figure 4 is a cross-sectional view of a clothes dryer in accordance with a first alternative embodiment of the present invention.

Figure 5 is a cross-sectional view of a cooling air inlet structure for a clothes dryer in accordance with a second alternative embodiment of the present invention.

Figure 6 is a cross-sectional view of a clothes dryer in accordance with a second alternative embodiment of the present invention.

Figure 7 is a cross-sectional view of a cooling air inlet structure for a clothes dryer in accordance with a third alternative embodiment of the present invention.

Figure 8 is a cross-sectional view of a cooling air inlet structure for a clothes dryer in accordance with a fourth alternative embodiment of the present invention.

Figure 9 is a cross-sectional view of a cooling air inlet structure for a clothes dryer in accordance with a fifth alternative embodiment of the present invention.

Figure 10 is a graph of noise frequency and transmission loss.

Figure 11 is a graph of the inner diameter of the inlet duct and the average amount of noise reduction.

Figure 12 is a graph of the wall thickness of the inlet duct and the average amount of noise reduction.

Figure 13 is a graph of the length of the inlet duct and the average amount of noise reduction.

Figure 14 is a graph of the aperture of the bore of the inlet duct and the average amount of noise reduction.

Figure 15 is a graph of the perforation ratio of the inlet duct and the average amount of noise reduction.

Reference mark:

Dryer 1, body 10, inner circulation air guiding device 20, cooling air inlet structure 30, outer circulation air guiding device 40, condenser 50, driving device 60, outer casing 100, expansion chamber 110, housing 120, peripheral wall 121, end wall 122, seal 130, air inlet duct 200, air inlet passage 210, perforation 220, first section 230, second section 240, partition 300, subchamber 310.

Detailed ways

The embodiments of the present invention are described in detail below, and the examples of the embodiments are illustrated in the drawings, wherein the same or similar reference numerals are used to refer to the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are intended to be illustrative of the invention and are not to be construed as limiting.

In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", " After, "Left", "Right", "Vertical", "Horizontal", "Top", "Bottom", "Inside", "Outside", "Clockwise", "Counterclockwise", "Axial", The orientation or positional relationship of the "radial", "circumferential" and the like is based on the orientation or positional relationship shown in the drawings, and is merely for convenience of description of the present invention and simplified description, and does not indicate or imply the indicated device or component. It must be constructed and operated in a particular orientation, and is not to be construed as limiting the invention. Furthermore, features defining "first" and "second" may include one or more of the features, either explicitly or implicitly. In the description of the present invention, "a plurality" means two or more unless otherwise stated.

In the description of the present invention, it should be noted that the terms "installation", "connected", and "connected" are to be understood broadly, and may be fixed or detachable, for example, unless otherwise explicitly defined and defined. Connected, or integrally connected; can be mechanical or electrical; can be directly connected, or indirectly connected through an intermediate medium, can be the internal communication of the two components. The specific meaning of the above terms in the present invention can be understood in a specific case by those skilled in the art.

A clothes dryer 1 according to an embodiment of the present invention will be described below with reference to the drawings.

As shown in FIGS. 1-9, a clothes dryer 1 according to an embodiment of the present invention includes a cooling wind inlet structure 30.

Among them, the clothes dryer 1 is a condensing type clothes dryer.

Specifically, as shown in FIGS. 4 and 6, the clothes dryer 1 includes a body 10, an inner circulation system, an outer circulation system, a water receiving box (not shown), and a driving device 60.

The body 10 has a drying chamber (not shown). The inner circulation system is mounted to the body 10 and includes an inner circulation air guiding device 20 (such as an impeller) and a heating device (not shown, such as a resistance wire), and the inner circulation air guiding device 20 is used to make the drying chamber The air inside is circulated, and the circulating air is heated while flowing through the heating device, and the heated air evaporates the moisture of the laundry in the drying chamber to become hot and humid air. The outer circulation system is mounted to the body 10 and includes a cooling wind inlet structure 30, an outer circulation air guiding device 40 (such as an impeller), and a condenser 50. The outer circulation air guiding device 40 is for guiding the air sucked by the cooling air intake structure 30 to the condenser 50 to cool the condenser 50 for condensing moisture in the moist hot air flowing therethrough into water droplets. The water receiving box is for holding water droplets on the condenser 50. A drive unit 60 (e.g., a motor) is separately coupled to the inner circulation air guide unit 20 and the outer circulation air guide unit 40 for driving the inner circulation air guide unit 20 and the outer circulation air guide unit 40.

Specifically, after the driving device 60 is operated, the inner circulation air guiding device 20 is operated to circulate the air in the drying chamber. The air in the drying chamber is heated as it flows through the heating device, thereby evaporating moisture in the laundry in the drying chamber to form moist hot air. When the driving device 60 is in operation, the external circulating air guiding device 40 is simultaneously operated, and the air is taken in from the outside through the cooling air inlet structure 30, and the air is blown onto the condenser 50 through the deflector or the like to cool the condenser 50, thereby The moist hot air in the drying chamber is cooled as it flows through the condenser 50, the water vapor recondenses into water droplets, and finally is taken into the water receiving box. The inner circulation system works in conjunction with the outer circulation system to dry the clothes.

A cooling air intake structure 30 according to an embodiment of the present invention will be described below with reference to the accompanying drawings.

As shown in FIGS. 1-9, a cooling wind inlet structure 30 according to an embodiment of the present invention includes an outer casing 100 and an inlet duct 200.

The air inlet duct 200 passes through the outer casing 100, and the air inlet duct 200 defines an air inlet passage 210. The outer casing 100 and the outer peripheral wall surface of the air inlet duct 200 jointly define an expansion chamber 110, and the peripheral wall of the air inlet duct 200 is provided with communication. The inlet passage 210 and the plurality of perforations 220 of the expansion chamber 110, wherein "several" includes one or more. There is no obstruction in the tube of the air inlet duct 200. When the outer circulation air guiding device 40 is in operation, outside air is drawn into the outer circulation air guiding device 40 from the air inlet duct 210.

According to the cooling air inlet structure 30 of the embodiment of the present invention, the expansion duct 110 is defined by the air inlet duct 200 and the outer casing 100 by providing the air inlet duct 200 and the outer casing 100, and the peripheral wall of the air inlet duct 200 is provided with communication. The inlet passage 210 and the perforation 220 of the expansion chamber 110, each perforation 220 on the inlet duct 200 can be regarded as an independent micro-pipe having a certain mass (corresponding to the quality of the vibration system). When the noise in the air inlet passage 210 is affected, the air in the micro duct will move, and the friction between the air in the micro duct and the hole wall of the through hole 220 will cause energy loss (corresponding to the damping of the vibration system), and the inside of the expansion chamber 110 When the air is disturbed by the air in the micro-pipe, compression and stretching (corresponding to the spring of the vibration system) occur, whereby the air in the perforation 220 of the inlet duct 200, the hole wall of the perforation 220 and the expansion chamber 110 are common. A vibration system is constructed, the natural frequency of which is close to the frequency of the noise, so that the air in the perforation 220 resonates under the action of noise, and then the friction is lost through the friction with the hole wall of the perforation 220. Energy, and ultimately serve the purpose of noise reduction. Therefore, the cooling air intake structure 30 for the dryer according to the embodiment of the present invention can reduce the wind noise of the cooling air, thereby achieving a noise reduction effect on the whole machine.

The clothes dryer 1 according to the embodiment of the present invention has an advantage of being low in noise by utilizing the cooling air intake structure 30 for a clothes dryer according to the above-described embodiment of the present invention.

A cooling air intake structure 30 for a clothes dryer in accordance with an embodiment of the present invention will now be described with reference to the accompanying drawings.

In some specific embodiments of the present invention, as shown in FIG. 2, in order to further improve the noise reduction effect, the plurality of through holes 220 are arranged in a plurality of rows and columns on the peripheral wall of the air inlet duct 200. Each row of perforations 220 are arranged along the circumferential direction of the inlet duct 200, and a plurality of rows of perforations 220 are spaced along the axial direction of the inlet duct 200. Each row of perforations 220 are arranged along the axial direction of the inlet duct 200, and a plurality of rows of perforations 220 are spaced along the circumferential direction of the inlet duct 200.

In some specific examples of the invention, as shown in FIG. 2, the outer casing 100 includes a housing 120 and a seal 130.

The housing 120 includes a peripheral wall 121 and an end wall 122 connected to one end of the peripheral wall 121. The peripheral wall 121 is disposed around the inlet duct 200. The inlet duct 200 passes through the end wall 122, and the end wall 122 is adjacent to one end of the inlet duct 200 and is adjacent thereto. The outer peripheral wall surface of the air duct 200 is sealingly connected. The air inlet duct 200 passes through the sealing member 130, and the sealing member 130 is adjacent to the other end of the air inlet duct 200. The sealing member 130 is sealingly connected to the outer peripheral wall surface of the air inlet duct 200 and the other end of the peripheral wall 121, respectively. Therefore, the housing 120, the sealing member 130 and the air inlet tube 200 can be used to define a relatively sealed expansion chamber 110, and the expansion chamber 110 is disposed around the air inlet passage 210 to improve the noise reduction effect. Here, the "relative sealing" means The remaining position of the expansion chamber 110 is sealed except for the position where the perforation 220 communicates with the inlet passage 210.

Further, the central axis of the housing 120, the central axis of the seal 130, and the central axis of the inlet duct 200 coincide. At least two of the housing 120, the seal 130, and the inlet duct 200 are integrally formed.

For example, the housing 120, the sealing member 130 and the air inlet tube 200 may be integrally formed by a mold, or may be inserted into the air inlet tube 200 on the basis of the housing 120 and the sealing member 130, and may also be inserted into the air duct. The seal member 130 is integrally formed and placed in the housing 120. The present invention does not specifically limit the manner in which the cooling air intake structure 30 is formed. In a preferred embodiment, the duct 200 and the seal member 130 are integrally formed and placed in the housing 120. This arrangement can reduce the difficulty of manufacturing and assembly, and is conducive to cost saving.

In some embodiments of the present invention, as shown in FIGS. 3 and 4, the inlet duct 200 has a plurality of sections arranged in the axial direction of the inlet duct 200, wherein the perforation ratio of any two sections and/or the cross section of the perforations 220 The cross-sectional area is different. In other words, the air inlet duct 200 may be formed by connecting two or more sections of pipes, and at least two of the ducts have different perforation characteristics, and the difference in perforation characteristics herein means that the cross-sectional area of the single perforation 220 and the perforation ratio are at least the same. different.

It will be understood by those skilled in the art that the perforation ratio of the inlet duct 200 refers to the ratio of the sum of the cross-sectional areas of all the perforations 220 on the inlet duct 200 to the surface area of the outer peripheral surface of the inlet duct 200.

This can increase the noise reduction bandwidth, thereby increasing the total noise reduction.

For example, as shown in FIG. 3, the intake duct 200 has a first section 230 and a second section 240, the cross-sectional area of the single perforation 220 of the first section 230 and the cross-sectional area of the single perforation 220 of the second section 240. Different, and the perforation ratio of the first segment 230 is different from the perforation ratio of the second segment 240.

In some specific examples of the present invention, as shown in FIGS. 5 and 6, the cooling air inlet structure 30 further includes a partition 300, and the partition 300 is disposed in the expansion chamber 110 and divides the expansion chamber 110 into a plurality of sub-chambers respectively. In chamber 310, each subchamber 310 is in communication with the inlet passage 210 through a perforation 220. This can significantly increase the total noise reduction.

Alternatively, the number of the spacers 300 may be 1-3. For example, as shown in FIG. 5, the expansion chamber 110 is provided with a partition 300 disposed around the inlet duct 200 and located at the center of the expansion chamber 110 in the axial direction of the expansion chamber 110. 300 divides the expansion chamber 110 into two annular sub-chambers 310 of the same volume.

In some embodiments of the present invention, as shown in FIGS. 7 and 8, the cross-sectional areas of the expansion chambers 110 in at least two portions of the portions in the axial direction of the expansion chamber 110 are different. Thereby, the thickness of the air layer outside the perforation 220 can be made inconsistent, so that the noise reduction bandwidth can be increased, thereby increasing the total noise reduction.

In some specific examples of the present invention, as shown in FIG. 7, the cross-sectional area of the expansion chamber 110 is graded in the axial direction of the expansion chamber 110. Specifically, the cross-sectional area of at least one of the intake duct 200 and the outer casing 100 is gradually changed in the respective axial directions. That is, it is possible to adopt a gradient diameter inlet duct 200 and/or a gradient diameter outer casing 100.

For example, in the example shown in FIG. 7, the inlet duct 200 is tapered in cross-sectional area, and the cross-sectional area of the outer casing 100 is constant. The cross-sectional line of the longitudinal section of the air inlet duct 200 may be a straight line, or may be a variety of smooth curves such as an exponential curve and a catenary curve.

Of course, it is also possible to use the outer casing 100 having a gradual cross-sectional area while keeping the cross-sectional area of the inlet duct 200 constant. It is also possible to simultaneously employ the outer casing 100 having a gradual cross-sectional area and the inlet duct 200 having a gradual cross-sectional area.

In some specific examples of the present invention, as shown in FIG. 8, the cross-sectional area of the expansion chamber 110 is abrupt in the axial direction of the expansion chamber 110. Specifically, the cross-sectional area of at least one of the intake duct 200 and the outer casing 100 is abruptly changed in the respective axial directions. That is, it is possible to adopt an air inlet tube 200 of a mutant diameter and/or an outer casing 100 of a mutant diameter.

For example, in the example shown in FIG. 8, the cross-sectional area of the air inlet duct 200 is abrupt, that is, the structure of the peripheral wall of the air inlet duct 200 is configured with a right-angled step, and the cross-sectional area of the outer casing 100 remains unchanged, whereby the air inlet duct 200 is mutated into two different diameters. In practical applications, the number of mutant diameters of the inlet duct 200 is usually not more than four.

Of course, it is also possible to use the outer casing 100 with abrupt cross-sectional area to keep the cross-sectional area of the inlet duct 200 constant. It is also possible to simultaneously employ the outer casing 100 having abrupt cross-sectional area and the inlet duct 200 having abrupt cross-sectional area.

In some specific examples of the present invention, as shown in FIG. 9, the air inlet duct 200 is a plurality of tubes having different diameters, and the plurality of air inlet ducts 200 are coaxially disposed, that is, the plurality of air inlet ducts 200 are sleeved together. This can increase the amount of noise reduction.

Wherein, for any two inlet ducts 200, the cross-sectional areas of the single perforations 220 may be the same or different, and the perforation ratios may be the same or different.

For example, in the example shown in FIG. 9, the inlet duct 200 is two and the pipe diameter is different, the two inlet ducts 200 are coaxially sleeved together, and the cross-sectional area and the perforation ratio of the single perforations 220 of the two inlet ducts 200 are different. Similarly, the cross-sectional area and perforation ratio of a single perforation 220 of each inlet duct 200 are also the same.

When the cooling air inlet structure 30 is specifically designed, the relationship between the cost, the space and the aerodynamic performance, and the amount of noise reduction of the cooling air inlet structure 30 is comprehensively considered.

The structural parameters of the cooling air inlet structure 30 are: the inner diameter D of the inlet duct 200, the wall thickness t of the inlet duct 200, the length L of the inlet duct 200, the outer diameter DP of the expansion chamber 110, the aperture d of the perforation 220, The perforation ratio δ affects the noise reduction characteristics. If the above parameters are used with different values, the noise reduction characteristics of the cooling wind inlet structure 30 will also change. For example, as shown in FIG. 10, the solid line in the figure is D=70, DP=160, L=200; t=1; d=1; the transmission loss (noise reduction amount) curve at δ=3%, the broken line is D=80, DP=180, L=160; t=0.5; d=2; transmission loss (noise reduction amount) curve at δ=4%.

As can be seen from Fig. 10, the transmission loss TL is a function of the frequency f and can be written as TL = y(f). The transmission loss curve is more complicated and consists of one valley. The transmission loss reflects the above two air intake structures 30 using different parameters. The degree of noise reduction at each frequency, the higher the transmission loss, indicating that the noise reduction effect is better. At some frequencies, the air intake structure 30 shown by the solid line has a good noise reduction effect; at some frequencies, the air intake structure 30 shown by the broken line has a good noise reduction effect. However, in the entire frequency band, it is difficult to intuitively indicate which of the air intake ducts 200 has a better noise reduction effect. Therefore, a simple noise reduction evaluation target is needed. From the energy point of view, the average noise reduction Z in the band [a, a+1, a+2, ... b] is defined as follows:

For the wind noise of the external circulation system of the dryer, the noise is a broadband noise, and the noise energy is widely distributed at 300 to 4000 Hz and above, but mainly concentrated at 300 to 3000 Hz. Therefore, define the average noise reduction as:

Through the simulation analysis, different inner diameter D of the air inlet duct 200, wall thickness t of the air inlet duct 200, length L of the air inlet duct 200, outer diameter DP of the expansion chamber 110, aperture d of the perforation 220, and perforation ratio δ are obtained. The average muffling amount Z _{0 is} obtained, thereby obtaining a preferred range of partial variables. details as follows:

When the wall thickness t of the air inlet duct 200, the length L of the air inlet duct 200, the outer diameter DP of the expansion chamber 110, the aperture d of the through hole 220, and the perforation ratio δ are fixed, the inner diameter D of the different air inlet duct 200 is adopted. Will get a different average noise reduction Z ₀ . Specifically, when t=1, L=200, DP=200, d=0.5, and δ=2%, the average muffling amount Z ₀ shown in FIG. 11 can be obtained by using the inner diameter D of the different air inlet duct 200.

As can be seen from Fig. 11, as the inner diameter D of the inlet duct 200 increases, the average muffling amount Z _{0 is} generally downward. Since the inner diameter D is too small, the cross-sectional area of the intake passage 210 is affected, resulting in a decrease in the amount of air, which may weaken the condensation effect to the condenser 50.

Therefore, in order to ensure that the air volume of the outer circulation system remains unchanged, in a preferred embodiment, the inner diameter D of the air inlet duct 200 ranges from 0.7 to 1.2 times the outer diameter of the outer circulation air guiding device 40 (such as a fan).

For the selection of the outer diameter DP of the expansion chamber 110, the following considerations are required. The thickness N of the air layer in the expansion chamber 110 has a significant effect on noise reduction. There are more medium and low frequency noises in the wind noise. The larger air layer thickness N can achieve better noise reduction effect. In order to ensure the basic noise reduction effect, the air layer thickness is preferably N≥20mm. In order to ensure a sufficient air thickness, the outer diameter DP of the expansion chamber 110 should take the maximum allowed by the structural space. However, due to the overall size of the dryer, the volume of the expansion chamber 110 generally does not exceed 25L. Taking the expansion chamber 110 as a circular columnar structure as an example, it is preferable that the outer diameter of the expansion chamber 110 is DP ≤ 200 mm, and similarly, the axial depth of the expansion chamber 110 is ≤ 250 mm.

When the inner diameter D of the air inlet duct 200, the length L of the air inlet duct 200, the outer diameter DP of the expansion chamber 110, the aperture d of the through hole 220, and the perforation ratio δ are fixed, different wall thicknesses of the air inlet duct 200 are employed. Will get a different average noise reduction Z ₀ . Specifically, when D=80; L=200, DP=200, d=0.5, δ=2%, the wall thickness t of the different air inlet duct 200 can be used to obtain the average noise reduction amount Z ₀ as shown in FIG. .

As can be seen from FIG. 12, as the wall thickness t of the inlet duct 200 increases, the average muffling amount Z ₀ increases first and then decreases. When the wall thickness t of the inlet duct 200 is greater than 1 mm, the overall decreasing trend is observed. Considering the processing factors of the mold product, a lower processing cost is obtained. If the air inlet duct 200 is made of metal, the wall thickness t of the air inlet duct 200 is 0.2 to 1.5 mm; if the air inlet duct 200 is made of plastic, The wall thickness t of the air inlet duct 200 is 2 to 4 mm.

When the inner diameter D of the air inlet duct 200, the wall thickness t of the air inlet duct 200, the outer diameter DP of the expansion chamber 110, the aperture d of the through hole 220, and the perforation ratio δ are fixed, the length L of the different air inlet duct 200 is adopted. Will get a different average noise reduction Z ₀ . Specifically, when D=80, t=1, DP=200, d=0.5, and δ=2%, the average muffling amount Z ₀ as shown in FIG. 13 can be obtained by using the length L of the different air inlet duct 200.

As can be seen from Fig. 13, as the length L of the inlet duct 200 increases, the average muffling amount Z _{0 is} generally on the rise. Due to the influence of the appearance of the dryer structure, the length L of the inlet duct 300 is ≤ 200 mm. The length of the long inlet duct 200 also easily affects the compactness and appearance of the dryer. Of course, the length L of the inlet duct 200 can be further reduced in the range of 90 mm to 150 mm, so that the structure is more compact and does not affect the appearance of the dryer and the arrangement of other components, as will be explained in detail below.

The outer diameter DP of the expansion chamber 110 is adopted when the inner diameter D of the inlet duct 200, the wall thickness t of the inlet duct 200, the length L of the inlet duct 200, the outer diameter DP of the expansion chamber 110, and the perforation ratio δ remain unchanged. The aperture d of the different perforations 220 will result in a different average muffling amount Z ₀ . Specifically, when D=80, t=1, DP=200, L=200, and δ=2%, the average muffling amount Z ₀ as shown in FIG. 14 can be obtained by using the aperture d of the different perforations 220.

As can be seen from Fig. 14, as the aperture d of the perforation 220 increases, the average muffling amount Z ₀ generally decreases.

According to Fig. 14, in theory, a structure in which the aperture d of the perforation 220 is ≤ 1 mm should be employed. However, in order to reduce the processing difficulty and reduce the processing cost, the above-mentioned aperture range is broken and optimized. Specifically, it is preferable that the hole diameter d of the perforation 220 is ≥ 2.5 mm. In the case where the hole diameter d of the perforation 220 is ≥ 2.5 mm, a better noise reduction effect is obtained by adjusting the perforation ratio δ and the length L of the inlet duct 200. Specifically, the noise reduction effect of the preferred value of the aperture d of the through hole 220 is d=0.5 mm as a reference. Compared with the whole machine sound power 72dbA when the perforation and expansion chamber are not provided, the theoretical noise reduction effect of the aperture d of the perforation 220 is preferably d=0.5mm.

According to the above table, if the preferred value d = 0.5 mm of the aperture d of the perforation 220 is theoretically selected, the sound power of the whole machine is reduced by 3.7 db, which is equivalent to a decrease of 57.3% in acoustic energy.

With the same wall thickness t, the inner diameter D of the inlet duct, and the outer diameter DP of the expansion chamber 110, if the hole diameter d of the perforation 220 is ≥ 2.5 mm, it is still possible to obtain a hole diameter d = 0.5 mm which is theoretically preferred to the perforation 220. Noise reduction effect. At the same time, it can greatly reduce the processing difficulty and reduce the processing cost. The specific noise reduction effect is as follows:

According to the above table, after breaking through the theoretical preferred range of less than or equal to 1 mm, when the aperture d≥2.5 mm of the perforation 220 is selected, the noise reduction effect of 3.3-3.8 dbA can still be obtained, which is equivalent to a decrease of 53.2% of the acoustic energy. 58.1%. That is to say, when the aperture d of the perforation 220 is preferably ≥ 2.5 mm, a noise reduction effect similar to or even superior to the theoretically preferable range can be achieved.

Of course, the present invention is not limited thereto, and the through hole 220 may be other shapes than the circular hole, such as a rectangular hole, a triangular hole, or the like, a cross-sectional area of the circular hole corresponding to the hole diameter d ≥ 2.5 mm of the through hole 220, and other shapes ( The perforation 220 of the circular hole, of course, also has a cross-sectional area of ≥19.6 mm ² .

According to the above table, the length L of the inlet duct 200 can be further preferably reduced in the range of 90 mm to 150 mm, thereby making the structure more compact and without affecting the appearance of the dryer and the arrangement of other components.

When the inner diameter D of the inlet duct 200, the wall thickness t of the inlet duct 200, the length L of the inlet duct 200, the outer diameter DP of the expansion chamber 110, and the aperture d of the perforation 220 remain unchanged, different perforation ratios δ are employed. Will get a different average noise reduction Z ₀ . Specifically, when D=80, t=1, DP=200, L=200, and d=0.5, the average muffling amount Z ₀ as shown in FIG. 15 can be obtained by using different perforation ratios δ. As can be seen from Fig. 15, as the perforation ratio δ of the inlet duct 200 increases, the variation of the average muffling amount Z ₀ is diverse.

In addition, as the aperture d of the perforation 220 increases, the preferred perforation ratio δ increases correspondingly, and even a 30% perforation ratio δ does not increase the processing difficulty or increase the processing cost, and the strength of the inlet duct 200 The requirements are not high and therefore do not affect the strength and structural reliability of the intake duct 200. With the increase of the aperture d of the perforation 220, the processing difficulty can be greatly reduced and the processing cost can be reduced.

A cooling wind inlet structure 30 in accordance with an embodiment of the present invention is described below.

The cooling air intake structure 30 according to an embodiment of the present invention includes an outer casing 100 and an air intake duct 200.

The outer casing 100 is disposed on the air inlet duct 200, and the air inlet duct 200 defines an air inlet passage 210. The outer casing 100 and the outer peripheral wall surface of the air inlet duct 200 jointly define an expansion chamber 110, and the peripheral wall of the air inlet duct 200 is disposed. There are a plurality of perforations 220 that connect the inlet passage 210 and the expansion chamber 110, wherein "several" includes one or more. There is no obstruction in the tube of the air inlet duct 200. When the outer circulation air guiding device 40 is in operation, outside air is drawn into the outer circulation air guiding device 40 from the air inlet duct 210. The cross-sectional area of each of the perforations 220 is greater than or equal to 19.6 mm ² .

According to the cooling wind inlet structure 30 of the embodiment of the invention, the wind noise of the cooling wind can be reduced, and the optimal noise reduction effect is achieved, thereby achieving a noise reduction effect on the whole machine.

The outer casing 100 is disposed on the air inlet duct 200, and the air inlet duct 200 defines an air inlet passage 210. The outer casing 100 and the outer peripheral wall surface of the air inlet duct 200 jointly define an expansion chamber 110, and the peripheral wall of the air inlet duct 200 is disposed. There are a plurality of perforations 220 that connect the inlet passage 210 and the expansion chamber 110, wherein "several" includes one or more. There is no obstruction in the tube of the air inlet duct 200. When the outer circulation air guiding device 40 is in operation, outside air is drawn into the outer circulation air guiding device 40 from the air inlet duct 210. The perforations 220 are circular holes having a diameter greater than or equal to 2.5 mm.

Other configurations and operations of the dryer 1 according to embodiments of the present invention are known to those of ordinary skill in the art and will not be described in detail herein.

In the description of the present specification, the description with reference to the terms "one embodiment", "some embodiments", "illustrative embodiment", "example", "specific example", or "some examples", etc. Particular features, structures, materials or features described in the examples or examples are included in at least one embodiment or example of the invention. In the present specification, the schematic representation of the above terms does not necessarily mean the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in a suitable manner in any one or more embodiments or examples.

While the embodiments of the present invention have been shown and described, the embodiments of the invention may The scope of the invention is defined by the claims and their equivalents.

Claims

A cooling air inlet structure for a clothes dryer, comprising:

Outer casing

An air inlet duct, the air inlet duct passes through the outer casing, the air inlet duct defines an air inlet passage, and the outer casing shell and the outer peripheral wall surface of the air inlet duct jointly define an expansion chamber, and the air inlet duct The peripheral wall of the tube is provided with a plurality of perforations that communicate the inlet passage and the expansion chamber.
A cooling air inlet structure for a clothes dryer, comprising:

An air inlet duct, wherein the air inlet duct defines an air inlet passage;

An outer casing, the outer casing is disposed on the air inlet pipe;

The outer casing and the outer peripheral wall surface of the air inlet duct jointly define an expansion chamber, and the peripheral wall of the air inlet tube is provided with a plurality of perforations communicating with the air inlet passage and the expansion chamber, each of the perforations The cross-sectional area is greater than or equal to 19.6 mm 2 .
A cooling air inlet structure for a clothes dryer, comprising:

An air inlet duct, wherein the air inlet duct defines an air inlet passage;

An outer casing, the outer casing is disposed on the air inlet pipe;

The outer casing and the outer peripheral wall surface of the air inlet duct jointly define an expansion chamber, and the peripheral wall of the air inlet tube is provided with a plurality of perforations communicating with the air inlet passage and the expansion chamber, the perforations being larger than a diameter Or a circular hole equal to 2.5mm.
A cooling air inlet structure for a clothes dryer according to claim 2 or 3, wherein said air inlet duct passes through said outer casing.
The cooling air inlet structure for a clothes dryer according to any one of claims 1 to 4, wherein the outer casing comprises:

a housing comprising a peripheral wall and an end wall connected to one end of the peripheral wall, the peripheral wall being disposed around the inlet duct, the inlet duct passing through the end wall, the end wall being adjacent to the end wall One end of the air duct is connected to the outer peripheral wall surface of the air inlet duct;

a sealing member, the inlet duct passing through the seal, the seal being adjacent to the other end of the inlet duct, the seal being respectively opposite to an outer peripheral wall surface of the inlet duct and the other end of the peripheral wall Sealed connection.
A cooling wind inlet structure for a clothes dryer according to claim 5, wherein at least two of said casing, said seal member and said inlet duct are integrally formed.
The cooling air inlet structure for a clothes dryer according to any one of claims 1 to 6, wherein the perforations are arranged along the peripheral wall of the air inlet duct along the air inlet duct A plurality of rows axially spaced apart and a plurality of rows spaced circumferentially along the inlet duct.
The cooling air inlet structure for a clothes dryer according to any one of claims 1 to 7, wherein the air inlet pipe has a plurality of sections arranged along an axial direction thereof, and a perforation ratio of any two of the sections The cross-sectional area of the perforations is different.
A cooling air inlet structure for a clothes dryer according to any one of claims 1 to 7, further comprising a partition, the partition being disposed in the expansion chamber and expanding the expansion The cavity is divided into a plurality of sub-chambers that communicate with the air inlet passage through the perforations, respectively.
A cooling air inlet structure for a clothes dryer according to any one of claims 1 to 7, wherein a cross-sectional area of at least two of the portions of the expansion chamber in the axial direction thereof different.
The cooling air inlet structure for a clothes dryer according to claim 10, wherein a cross-sectional area of said expansion chamber is gradually changed in an axial direction thereof.
The cooling air inlet structure for a clothes dryer according to claim 11, wherein a cross-sectional area of at least one of the air inlet duct and the outer casing is gradually changed in an axial direction thereof.
A cooling air inlet structure for a clothes dryer according to claim 10, wherein a cross sectional area of said expansion chamber is abrupt in its axial direction.
A cooling wind inlet structure for a clothes dryer according to claim 13, wherein a cross-sectional area of at least one of said intake duct and said outer casing is abrupt in its axial direction.
The cooling air inlet structure for a clothes dryer according to any one of claims 1 to 7, wherein the air inlet ducts are a plurality of coaxially disposed.
The cooling air inlet structure for a clothes dryer according to any one of claims 1 to 9, wherein an inner diameter of the air inlet duct is 0.7 of an outer diameter of the outer circulation air guiding device. ~ 12.2 times.
The cooling air inlet structure for a clothes dryer according to any one of claims 1 to 9, wherein the length of the air inlet duct in the axial direction thereof is less than or equal to 200 mm.
A cooling air inlet structure for a clothes dryer according to claim 17, wherein said inlet duct has a length in the axial direction of 90 to 150 mm.
The cooling air inlet structure for a clothes dryer according to any one of claims 1 to 9, wherein the expansion chamber has a circular cross section, and the expansion chamber The outer diameter is less than or equal to 200 mm, and the depth of the expansion chamber along its axial direction is less than or equal to 250 mm.
The cooling air inlet structure for a clothes dryer according to any one of claims 1-9, 16-19, wherein the air inlet pipe is a metal pipe, and the wall thickness of the air inlet pipe 0.2 to 1.5 mm; or

The air inlet pipe is a plastic pipe, and the air inlet pipe has a wall thickness of 2 to 4 mm.
The cooling air inlet structure for a clothes dryer according to any one of claims 1 to 9, wherein the thickness of the air layer in the expansion chamber is 20 mm or more.
A clothes dryer characterized by comprising a cooling air inlet structure for a clothes dryer according to any one of claims 1 to 21.
A clothes dryer according to claim 22, wherein said clothes dryer is a condensing type clothes dryer.
The clothes dryer of claim 23, comprising:

a body having a dry clothes chamber therein;

An internal circulation system installed in the body and including an inner circulation air guiding device and a heating device, wherein the inner circulation air guiding device is configured to circulate air in the drying chamber, circulating circulating air When flowing through the heating device, the heated air evaporates the moisture of the laundry in the drying chamber to become hot and humid air;

An outer circulation system, the outer circulation system being mounted to the body and comprising the cooling air inlet structure, an outer circulation air guiding device and a condenser, the outer circulation air guiding device being used for being sucked by the air inlet passage Air is directed to the condenser to cool the condenser, the condenser for condensing moisture in the moist hot air flowing therethrough into water droplets;

a water receiving box for holding water droplets on the condenser;

a driving device, wherein the driving device is respectively drivingly connected to the inner circulation air guiding device and the outer circulation air guiding device.