Air outlet structure of an air circulating machine and air circulating machine

Abstract

The application provides an air outlet structure of an air circulating machine and the air circulating machine. The air outlet structure comprises an air outlet member and an air guide structure. The air outlet member has a turbine air outlet channel. Two or more heat exchange wires are arranged on the air outlet member in sequence and at intervals. The interval between two adjacent heat exchange wires forms a wind channel. The air guide structure is used for introducing heat exchange gas to each heat exchange wire, so that the air outlet member can exchange heat with the heat exchange gas through each heat exchange wire. According to the technical scheme of the application, each heat exchange wire can increase the heat exchange area of the air outlet member, so as to improve the heat exchange efficiency of the air outlet member and the heat exchange gas, thereby improving the anti-icing effect of the air outlet member. In addition, the heat exchange structure formed by each heat exchange wire can also disturb the incoming flow to generate vortex, thereby increasing the heat exchange efficiency.

Description

An air outlet structure for an air circulator and an air circulator Technical Field

[0001] This invention belongs to the field of air circulator technology, specifically relating to an air outlet structure and an air circulator. Background Technology

[0002] An air circulator is used for compressed air circulation and cooling. The air circulator is driven by a turbine driven by high-pressure gas, which drives the rotor to rotate. The turbine and the compressor wheel are coaxial. After the compressor wheel compresses the air, the air temperature and pressure increase and enter the compressor volute. Then, the high-temperature and high-pressure air in the compressor volute passes through the turbine volute and enters the nozzle to increase speed, reduce pressure and drive the turbine to expand the air and cool it.

[0003] The air circulator includes an air outlet component, such as an air outlet duct, which has a turbine outlet passage through which the air circulator discharges air. Because the gas temperature inside the turbine outlet passage is low, the temperature of the air outlet component is also low, making it prone to icing. Currently, a common method to prevent icing is to introduce high-temperature heat exchange gas into the air outlet component using an induced draft structure. However, this heat exchange method currently has low efficiency and requires further improvement. Summary of the Invention

[0004] Therefore, the present invention provides an air outlet structure and an air circulator, and the main technical problem to be solved is: how to improve the heat exchange efficiency between the introduced heat exchange gas and the outlet component.

[0005] To solve the above problems, the present invention provides an air outlet structure for an air circulator, which includes an air outlet component and an air intake structure. The air outlet component has a turbine air outlet channel and is provided with two or more heat exchange wires arranged sequentially at intervals. The interval between two adjacent heat exchange wires forms an air passage.

[0006] The air intake structure is used to introduce heat exchange gas into each of the heat exchange wires, so that the air outlet can exchange heat with the heat exchange gas through each of the heat exchange wires.

[0007] In some embodiments, each of the heat exchange wires is a round wire with a diameter of d, wherein,

[0008] The distance between two adjacent heat exchange wires is S, and d and S satisfy the following: Where a = 6.45–6.7, b = 2.5–2.65, and the units for both d and S are millimeters;

[0009] And / or, the number of heat exchange wires is N, d 2*N+c1*d*N-c2*d=c3, where c1=9.1~9.30, c2=32~34, c3=87~95, and d is in millimeters.

[0010] In some embodiments, each of the heat exchange wires is bent to form an undulating structure; each of the heat exchange wires is connected to the air outlet via one side of its respective undulating direction.

[0011] In some embodiments, each of the heat exchange wires is sinusoidal in shape; for a single heat exchange wire, the heat exchange wire forms a first arc segment at the crest and a second arc segment at the trough; for adjacent first and second arc segments on the heat exchange wire, the height difference between the centers of the first and second arc segments is h1; and half the wavelength of the sine wave is w; where h1 = (1.2-1.5)*w, and both h1 and w are in millimeters.

[0012] In some embodiments, the air intake structure includes a heat exchange cavity disposed on the air outlet, the air intake structure introduces heat exchange gas through the heat exchange cavity, and the heat exchange cavity also has an air outlet;

[0013] Each of the heat exchange wires is located inside the heat exchange cavity, and each of the heat exchange wires is connected to the cavity wall of the heat exchange cavity so as to be connected to the air outlet through the cavity wall of the heat exchange cavity.

[0014] In some embodiments, the heat exchange chamber has an air inlet, through which the heat exchange gas is introduced; the heat exchange chamber has a first chamber wall and a second chamber wall opposite to each other, and the air inlet is disposed on the first chamber wall; wherein, when each of the heat exchange wires is bent to form an undulating structure, each of the heat exchange wires is disposed on the second chamber wall through one side of its respective undulating direction, and the other side of the undulating direction of each heat exchange wire protrudes from the second chamber wall.

[0015] In some embodiments, the heat exchange cavity is an annular cavity disposed within the wall thickness of the outlet component, and the annular cavity is arranged around the centerline of the turbine outlet passage.

[0016] Each of the heat exchange wires is annular and is fitted onto the annular cavity wall of the annular cavity.

[0017] In some embodiments, the air intake structure includes an air intake pipe through which heat exchange gas is introduced.

[0018] In some embodiments, the air intake pipe includes a first pipe section and a second pipe section connected together. The air intake pipe is disposed on the air outlet. The air intake pipe introduces heat exchange gas from the outside through the end of the first pipe section opposite to the second pipe section, and the air intake pipe guides the introduced heat exchange gas to each of the heat exchange wires through the end of the second pipe section opposite to the first pipe section. The first pipe section and the second pipe section are connected by an arc-shaped pipe section, wherein the radius of the arc-shaped pipe section is R, the inner hole of the air intake pipe is a circular hole, and the diameter of the circular hole is D, wherein R = 16-18 mm and D = 8-9.5 mm.

[0019] In some embodiments, when the air-guiding structure includes a heat exchange cavity disposed on the air outlet, and each of the heat exchange wires is located within the heat exchange cavity, each of the heat exchange wires is bent to form an undulating structure, each of the heat exchange wires is connected to the cavity wall of the heat exchange cavity through one side of its undulating direction, and the other side of the undulating direction of each heat exchange wire protrudes beyond the cavity wall, the air-guiding structure introduces heat exchange gas into the heat exchange cavity through the air-guiding pipe, so that the heat exchange cavity introduces heat exchange gas through the air-guiding pipe; the other side of the undulating direction of each heat exchange wire protrudes beyond the height h2 of the cavity wall, the spacing between two adjacent heat exchange wires is S, and the number of heat exchange wires is N; the inner hole of the air-guiding pipe is a circular hole, and the diameter of the circular hole is D; wherein, h2, S, and D are all measured in millimeters.

[0020] The present invention also provides an air circulator, which includes the air outlet structure of the air circulator described in any one of the above-mentioned methods.

[0021] The air outlet structure and air circulator provided by this invention have the following beneficial effects:

[0022] 1. Each heat exchange wire increases the heat exchange area of ​​the outlet component, thereby improving the heat exchange efficiency between the outlet component and the heat exchange gas, and thus enhancing the anti-icing effect of the outlet component. Furthermore, the airflow channel formed between adjacent heat exchange wires facilitates airflow, further improving heat exchange efficiency.

[0023] 2. The heat exchange structure formed by each heat exchange wire can disturb the incoming flow to generate eddies, thereby increasing the heat exchange efficiency. In addition, through the undulating structure design of the heat exchange wire, it can absorb sound and vibration very efficiently. When the sound is transmitted to the surface of the heat exchange wire, the heat exchange wire will vibrate, thereby converting the sound into heat energy, which has the effect of vibration reduction and noise reduction.

[0024] 3. By making the R of the air intake tube 16-18 mm and the D 8-9.5 mm, the air intake tube can have a lower sound pressure level fundamental frequency resonance peak, reducing the frequency response of the first-order resonant frequency of the air intake tube, thereby reducing the vibration and noise of the air intake tube. Attached Figure Description

[0025] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the accompanying drawings used in the description of the embodiments or the prior art will be briefly introduced below. The drawings described below are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0026] Figure 1 is a cross-sectional view of an air circulator provided in an embodiment of the present invention;

[0027] Figure 2 is a schematic diagram illustrating the structure of a single heat exchange wire according to an embodiment of the present invention;

[0028] Figure 3 is an enlarged view of point A in Figure 2;

[0029] Figure 4 is a schematic diagram reflecting the arrangement of two adjacent heat exchange wires according to an embodiment of the present invention;

[0030] Figure 5 is a graph showing the sound pressure level Lp of the fundamental frequency resonant peak of the air intake tube as a function of R and D.

[0031] Figure 6 shows a schematic diagram of the operating frequency of the first-order fundamental frequency resonance peak of the air duct between 1250Hz and 1550Hz when R=17 and D=9.

[0032] Figure 7 shows a schematic diagram of the operating frequency of the first-order fundamental frequency resonance peak of the air duct between 0-9000Hz when R=17 and D=9.

[0033] The attached figures are labeled as follows:

[0034] 1. Air outlet; 2. Heat exchange wire; 3. Turbine; 4. Air intake pipe; 5. Compressor volute; 6. Compressor impeller; 7. Turbine volute; 8. Nozzle; 11. Turbine wheel cover; 12. Sleeve; 21. First arc segment; 22. Second arc segment; 23. Air passage; 41. First pipe section; 42. Second pipe section; 43. Arc-shaped pipe section; 100. Turbine air outlet passage; 101. Heat exchange chamber; 102. Air intake port; 103. Air outlet; 111. Air outlet pipe; 1011. First chamber wall; 1012. Second chamber wall; 201. One side of the undulating direction of the heat exchange wire; 202. The other side of the undulating direction of the heat exchange wire. Detailed Implementation

[0035] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0036] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0037] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0038] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0039] Referring to Figures 1-2, according to an embodiment of the present invention, an air outlet structure for an air circulator is provided, comprising an air outlet component 1 and an air duct structure. The air outlet component 1 has a turbine air outlet channel 100, and two or more heat exchange wires 2 arranged sequentially at intervals are provided on the air outlet component 1, with the interval between adjacent heat exchange wires 2 forming an air passage 23. The aforementioned air duct structure is used to introduce heat exchange gas to each heat exchange wire 2, enabling the air outlet component 1 to exchange heat with the heat exchange gas through each heat exchange wire 2. In some embodiments, the aforementioned heat exchange gas can be the gas inside the compressor volute 5 of the air circulator. The gas inside the compressor volute 5 is a high-temperature gas, and when the gas inside the compressor volute 5 is introduced to each heat exchange wire 2, it can exchange heat with each heat exchange wire 2 using its own high temperature.

[0040] In the above example, each heat exchange wire 2 can increase the heat exchange area of ​​the outlet element 1, thereby improving the heat exchange efficiency between the outlet element 1 and the heat exchange gas, and thus improving the anti-icing effect of the outlet element 1. In addition, the air passage 23 formed between two adjacent heat exchange wires 2 is conducive to airflow, thereby further improving the heat exchange efficiency.

[0041] Compared with heat exchange components made of thin metal heat exchange fins, the heat exchange structure formed by each heat exchange wire 2 can save at least 50% of the material required to increase the heat exchange surface area under the same energy efficiency value. Correspondingly, the heat exchange efficiency can be significantly improved while keeping the material usage constant.

[0042] In some embodiments, each of the heat exchange wires 2 described above may be a metal wire.

[0043] It should be noted that the heat exchange structure formed by each heat exchange wire 2 can sometimes be called a heat exchange wire mesh, although the heat exchange wire mesh formed by each heat exchange wire 2 does not have the mesh structure of a conventional wire mesh.

[0044] The heat exchange structure formed by the heat exchange wires 2 can disturb the incoming flow to generate eddies, thereby increasing heat exchange efficiency, making it very suitable for microchannel heat exchange. Furthermore, this heat exchange structure can also promote the stability of the airflow, reduce large eddies and dead zones, and suppress and eliminate noise. The noise suppression and elimination mechanisms of this heat exchange structure are as follows: 1. When the airflow passes over the surface of the heat exchange structure, the structure interferes with the gas flow on the bluff body surface, reducing the local flow impact velocity; 2. The heat exchange structure decomposes the incoming flow into small eddies, causing changes in the downstream spanwise shedding eddies, reducing the orderliness of the eddies, and thus reducing certain types of turbulence or vibration; 3. The heat exchange structure removes eddies from the bluff body surface, dispersing sound wave energy, thereby reducing acoustic emission efficiency.

[0045] In some embodiments, as shown in Figure 4, each of the aforementioned heat exchange wires 2 can be a circular wire with a diameter of d, wherein the distance between two adjacent heat exchange wires 2 is S, and d and S satisfy the following: a = 6.45–6.7, b = 2.5–2.65, and the units for both d and S are millimeters.

[0046] In the example above, by making The relationship between the diameter d of the heat exchange wire and the spacing S between two adjacent heat exchange wires can be defined, so that the heat exchange wire 2 has a suitable spacing S when the diameter d is set. This allows the air passage 23 between two adjacent heat exchange wires 2 to maintain a suitable flow space, avoiding the situation where the flow space of the air passage 23 between two adjacent heat exchange wires 2 is too large, which would reduce the number of heat exchange wires 2 in the limited space, resulting in a smaller heat exchange area and affecting the heat exchange efficiency. It can also avoid the situation where the flow space of the air passage 23 between two adjacent heat exchange wires 2 is too small, which would obstruct the airflow, reduce the air volume, and result in a lower heat exchange efficiency.

[0047] In some embodiments, the number of heat exchange wires 2 can be N, where N and d satisfy:

[0048] d 2 *N+c1*d*N-c2*d=c3.

[0049] Where c1 = 9.1 to 9.30, c2 = 32 to 34, c3 = 87 to 95, and d is in millimeters.

[0050] In the example above, by making d 2 The formula *N + c1*d*N - c2*d = c3 defines the relationship between the diameter d of the heat exchanger wire 2 and the number N of the heat exchanger wires 2, ensuring that the heat exchanger wires 2 have a suitable diameter d when the number N is set. Specifically, when each heat exchanger wire 2 is installed within a limited heat exchange space, the number N of the heat exchanger wires 2 can be predetermined. The number N of the heat exchanger wires 2 should satisfy the condition that the heat exchanger wires 2 can fill the heat exchange surface of the outlet component 1 to improve heat exchange efficiency. Where the number of heat exchanger wires 2 is already determined, the above formula d can be used. 2 *N+c1*d*N-c2*d=c3 determines the diameter d of each heat exchange wire 2. This ensures that the diameter of each heat exchange wire 2 is not too large, which would affect the flow space of the air passage 23 between adjacent heat exchange wires 2, leading to obstructed airflow, reduced air volume, and lower heat exchange efficiency. Conversely, it also ensures that the diameter of each heat exchange wire 2 is not too small, which would reduce the heat exchange area of ​​the heat exchange wire 2 and result in lower heat exchange efficiency.

[0051] In some embodiments, each of the aforementioned heat exchange wires 2 can be bent to form an undulating structure. Each heat exchange wire 2 is connected to the air outlet 1 via one side of its respective undulating direction.

[0052] In the above example, as shown in Figure 3, the present invention designs the heat exchange wire 2 with an undulating structure, forming peaks and troughs on the heat exchange wire 2. The heat exchange wire 2 is connected to the air outlet 1 through the peak side or trough side. Compared with a straight heat exchange wire 2, the peaks or troughs of the heat exchange wire 2 of the present invention have a larger connection space, making it easier to connect the heat exchange wire 2 to the air outlet 1. In addition, the undulating structure design of the heat exchange wire 2 allows it to absorb sound and vibration very efficiently. When sound is conducted to the surface of the heat exchange wire 2, the heat exchange wire 2 will vibrate, thereby converting the sound into heat energy, achieving the effect of vibration reduction and noise reduction.

[0053] In some embodiments, as shown in Figure 3, each of the aforementioned heat exchange wires 2 can be sinusoidal in shape. For a single heat exchange wire 2, a first arc segment 21 is formed at the crest of the wave, and a second arc segment 22 is formed at the trough. For adjacent first arc segments 21 and second arc segments 22 on the heat exchange wire 2, the height difference between the centers of the first arc segment 21 and the second arc segment 22 is h1, and half the wavelength of the sine wave is w. Wherein, h1 = (1.2~1.5)*w, and the units of both h1 and w are millimeters.

[0054] In the above example, by limiting h1 = (1.2~1.5)*w, the amplitude height of the heat exchange wire 2 is not too small, which would result in a small heat exchange area and affect the heat exchange efficiency; it also prevents the amplitude height of the heat exchange wire 2 from being too large, which would occupy too much space and make it difficult to install in a narrow space.

[0055] In some embodiments, as shown in Figure 3, the radii of both the first arc segment 21 and the second arc segment 22 are r, where r = 0.8w to 1.3w. By limiting r to 0.8w to 1.3w, the amplitude height of the heat exchange wire 2 is restricted. The main purpose of this design is to prevent the amplitude height of the heat exchange wire 2 from being too small, resulting in a small heat exchange area and affecting heat exchange efficiency; and also to prevent the amplitude height of the heat exchange wire 2 from being too large, occupying too much space and making installation in confined spaces difficult.

[0056] In some embodiments, as shown in Figures 1 and 2, the aforementioned air intake structure may include a heat exchange chamber 101 disposed on the air outlet 1, through which the air intake structure introduces heat exchange gas. The heat exchange chamber 101 also has an air outlet 103, allowing the introduced heat exchange gas to flow within the heat exchange chamber 101, forming a flowing airflow, which facilitates heat exchange of the heat exchange wire 2. In a specific application example, the air outlet 103 may communicate with the interior of the turbine casing 7 of the air circulator. The gas that has undergone heat exchange within the heat exchange chamber 101 can enter the interior of the turbine casing 7 through the air outlet 103 to achieve gas recovery.

[0057] The aforementioned heat exchange wires 2 are located inside the heat exchange cavity 101, and each heat exchange wire 2 is connected to the cavity wall of the heat exchange cavity 101 so as to be connected to the air outlet 1 through the cavity wall of the heat exchange cavity 101.

[0058] In the above example, the heat exchange chamber 101 gathers the heat exchange gas inside, and by arranging each heat exchange wire 2 inside the heat exchange chamber 101, the efficiency of heat exchange between each heat exchange wire 2 and the heat exchange gas can be improved, thereby further improving the heat exchange efficiency between the gas outlet 1 and the heat exchange gas.

[0059] In some embodiments, as shown in Figures 2 and 3, the aforementioned heat exchange chamber 101 has an air inlet 102 through which the heat exchange chamber 101 introduces the aforementioned heat exchange gas. The heat exchange chamber 101 has opposing first chamber walls 1011 and second chamber walls 1012, and the air inlet 102 is disposed on the first chamber wall 1011. When each heat exchange wire 2 is bent to form an undulating structure, each heat exchange wire 2 is disposed on the second chamber wall 1012 through one side 201 of its respective undulating direction, and the other side 202 of the undulating direction of each heat exchange wire 2 protrudes from the second chamber wall 1012.

[0060] In the above example, the air intake 102 and the heat exchange wire 2 are located on opposite sides of the heat exchange cavity 101, so that when the airflow from the air intake 102 flows into the heat exchange cavity 101, it can impact the side of the heat exchange wire 2 that is away from the second cavity wall 1012. Since the heat exchange wire 2 has a wave-like undulating structure, the side of the heat exchange wire 2 that is away from the second cavity wall 1012 can undergo elastic deformation when impacted by the airflow from the air intake 102 to absorb sound and vibration, thereby achieving the effect of noise reduction.

[0061] In some embodiments, each of the heat exchange wires 2 can be brazed to the second cavity wall 1012 of the heat exchange cavity 101 via one side of its respective undulating direction. The molten brazing filler metal after brazing fills the gap between the heat exchange wire 2 and the second cavity wall 1012, ensuring contact between the second cavity wall 1012 and the heat exchange wire 2 to increase the heat transfer area.

[0062] In some embodiments, as shown in Figures 1 and 2, the aforementioned heat exchange cavity 101 can be an annular cavity disposed within the wall thickness of the air outlet member 1, and the annular cavity is arranged around the centerline of the turbine air outlet passage 100. Each of the aforementioned heat exchange wires 2 is annular and is sleeved on the annular cavity wall.

[0063] In the above example, the annular heat exchange cavity 101 can improve the heat exchange efficiency between the heat exchange gas and the outlet component 1. By designing the heat exchange wire 2 as annular and sleeved on the annular cavity wall, it is beneficial to increase the heat exchange area of ​​the heat exchange wire 2.

[0064] In some embodiments, the aforementioned air outlet 1 may include a turbine wheel cover 11 and a sleeve 12, the turbine wheel cover 11 having an air outlet pipe 111. The sleeve 12 is fitted over the outside of the air outlet pipe 111, forming the aforementioned annular cavity between the two. The inner bore of the air outlet pipe 111 forms at least a segment of the aforementioned turbine air outlet passage 100.

[0065] In the above example, by designing the air outlet 1 as a component, it is advantageous to form the aforementioned annular heat exchange cavity 101 within the wall thickness of the air outlet 1.

[0066] It should be noted that the sleeve 12 mentioned above can also be referred to as an outlet guide in some situations.

[0067] To facilitate the introduction of heat exchange gas into the aforementioned heat exchange chamber 101, in some embodiments, as shown in FIG1, the aforementioned gas induced structure may include a gas induced pipe 4, through which the gas induced structure introduces heat exchange gas.

[0068] The heat exchange gas mentioned above can be high-temperature, high-pressure gas compressed by the compressor wheel 6 of the air circulator. The bleed pipe 4 introduces this high-temperature, high-pressure gas to achieve heat exchange with the low-temperature wall surface of the turbine outlet passage 100. This increases the wall temperature of the turbine outlet passage 100 through fluid and solid heat transfer, thereby limiting icing of the outlet component 1. However, the bleed pipe 4 may resonate under certain conditions, potentially causing unnecessary vibration, which could affect structural integrity or cause noise problems. A high fundamental frequency resonant sound pressure level can cause high-level vibration in the bleed pipe 4, potentially leading to material fatigue and damage. A lower fundamental frequency resonant sound pressure level means less amplification of acoustic energy at a specific frequency, helping to reduce vibration and noise in the bleed pipe 4.

[0069] To achieve a lower fundamental frequency resonant sound pressure level in the air intake pipe 4 and reduce vibration and noise within it, in some embodiments, as shown in Figure 1, the aforementioned air intake pipe 4 includes a first pipe section 41 and a second pipe section 42 connected together, and is mounted on the air outlet 1. The air intake pipe 4 introduces heat exchange gas from the outside through the end of the first pipe section 41 opposite to the second pipe section 42, and guides the introduced heat exchange gas to each heat exchange wire 2 through the end of the second pipe section 42 opposite to the first pipe section 41. The first pipe section 41 and the second pipe section 42 are connected by an arc-shaped pipe section 43. The radius of the arc-shaped pipe section 43 is R, and the inner hole of the air intake pipe 4 is a circular hole with a diameter of D. R = 16–18 mm, and D = 8–9.5 mm.

[0070] In the above example, by setting R = 16-18 mm and D = 8-9.5 mm, the air intake tube 4 can have a lower sound pressure level fundamental frequency resonance peak, reducing the frequency response of the first-order resonant frequency of the air intake tube 4, thereby reducing the vibration and noise of the air intake tube 4, thus solving the problem of high-level noise that may be caused by the airflow of the air intake tube 4.

[0071] The following analyzes the process of obtaining R and D. Specifically, in order to solve the sound pressure level of the fundamental frequency resonance peak of the air intake tube 4, multiple simulations can be performed by changing the radius R of the arc-shaped tube segment 43 and the inner diameter D of the air intake tube 4. The influence of the two variables R and D on the resonance peak is obtained, and the mathematical relationship between R and D and the dependent variable, the fundamental frequency resonance peak, is obtained through polynomial regression.

[0072] Since changing the wall thickness T of the air intake tube 4 only has a slight effect on the resonance, the air intake tube 4 is designed only by optimizing R and D to reduce the sound pressure level of its fundamental frequency resonance peak. The frequency response of the air intake tube 4 is represented by the sound pressure level Lp of the air intake tube 4:

[0073]

[0074]

[0075] Where P ref The reference pressure is 20 μPa, where p is the sound pressure (Pa), and * denotes the conjugate complex number. The model parameters for the air intake tube are shown in Table 1 below.

[0076] Table 1

[0077] Name Value Pipe Wall Young's Modulus 6.84e10 [Pa] Pipe Wall Poisson's Ratio 0.3316 Ambient Temperature 184 (°C) Ambient Pressure 4.46~4.49 (bara) Average Flow Velocity 52.7 (m / s) surface

[0078] Through simulation calculations and function fitting, the sound pressure level Lp of the fundamental frequency resonant peak of air intake tube 4 is related to R and D as follows:

[0079] Lp=a1+a2*R+a3*D+a4*R2+a5*D2+a6*D*R;

[0080] Among them, a1=246.5±8.64, a2=-5.479±0.79, a3=-2.758±0.8, a4=0.154±0.02, a5=0.095±0.04, a6=0.031±0.03.

[0081] The function graphs of Lp, R and D are shown in Figure 5. As can be seen from Figure 5, within the given function interval, when R = 16-18 mm and D = 8-9.5 mm, the air duct 4 has a relatively small fundamental frequency resonance peak with a sound pressure level.

[0082] Figures 6 and 7 both show schematic diagrams relating the first-order fundamental frequency resonant peak of the air intake tube 4 to the operating frequency when R = 17 and D = 9. Figure 6 shows that when the operating frequency range is between 1250 Hz and 1550 Hz, the air intake tube 4 exhibits the largest resonant peak at 1425 Hz. Figure 7 shows that when the operating frequency range is between 0 and 9000 Hz, the air intake tube 4 has six first-order natural frequency resonant peaks. Furthermore, both Figures 6 and 7 demonstrate that when R = 17 and D = 9, the first-order fundamental frequency resonant peaks of the air intake tube 4 are relatively small, thus resulting in reduced vibration and noise.

[0083] In some embodiments, as shown in Figures 1-3, when the air intake structure includes a heat exchange cavity 101 disposed on the air outlet 1, and each heat exchange wire 2 is located within the heat exchange cavity 101, each heat wire is bent to form an undulating structure, each heat exchange wire 2 is connected to the cavity wall of the heat exchange cavity 101 through one side 201 of its respective undulating direction, and the other side 202 of the undulating direction of each heat exchange wire protrudes from the cavity wall, the air intake structure introduces heat exchange gas into the heat exchange cavity 101 through the air intake pipe 4, so that the heat exchange cavity 101 introduces heat exchange gas through the air intake pipe 4; the other side 202 of the undulating direction of each heat exchange wire protrudes from the cavity wall h2 at a height, the distance between two adjacent heat exchange wires 2 is S, and the number of heat exchange wires 2 is N. The inner hole of the air intake pipe 4 is a circular hole with a diameter of D. h2, S, and D are all measured in millimeters.

[0084] In the example above, by making The relationship between the flow cross-sectional area of ​​the air passage 23 between two adjacent heat exchange wires 2 and the flow cross-sectional area of ​​the air intake pipe 4 can be defined, so that the gas flow from the air intake pipe 4 can flow fully into the air passage 23 between each pair of adjacent heat exchange wires 2, avoiding the airflow obstruction caused by the flow cross-sectional area of ​​the air passage 23 between two adjacent heat exchange wires 2 being too small, which would affect the air volume and reduce the heat exchange efficiency.

[0085] It should be noted that in some implementations, h2 is equal to h1.

[0086] In some embodiments, the present invention also provides an air circulator, which may include the air outlet structure of any of the above-described air circulators. Because the air circulator employs the aforementioned air outlet structure, the heat exchange wire 2 can increase the heat exchange area of ​​the air outlet component 1, thereby improving the heat exchange efficiency between the air outlet component 1 and the heat exchange gas, and thus improving the anti-icing effect of the air outlet component 1.

[0087] The working principle of the air circulator of the present invention is as follows: As shown in Figure 1, the air circulator is used for compressed air circulation and cooling. The air circulator is driven by high-pressure gas to drive the turbine 3 to rotate the rotor. The turbine 3 and the compressor wheel 6 are coaxial. After the compressor wheel 6 compresses the air, the air temperature and pressure increase and enter the compressor volute 5. Then the high temperature and high pressure air in the compressor volute 5 passes through the turbine volute 7 and enters the nozzle 8 to increase speed, reduce pressure and drive the turbine 3 to expand the air for cooling.

[0088] It will be readily understood by those skilled in the art that, without conflict, the advantageous technical features of the above-mentioned methods can be freely combined and superimposed.

[0089] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. An air outlet structure for an air circulator, characterized in that: The device includes an exhaust component (1) and an exhaust structure. The exhaust component (1) has a turbine exhaust channel (100). The exhaust component (1) is provided with two or more heat exchange wires (2) arranged sequentially at intervals. The interval between two adjacent heat exchange wires (2) forms an air passage (23). The exhaust structure is used to introduce heat exchange gas into each of the heat exchange wires (2), so that the exhaust component (1) can exchange heat with the heat exchange gas through each of the heat exchange wires (2). Each of the heat exchange wires (2) is a circular wire with a diameter of d. The distance between two adjacent heat exchange wires (2) is S, and d and S satisfy the following: Where a = 6.45~6.7, b = 2.5~2.65, and both d and S are in millimeters; and / or, the number of heat exchange wires is N. Where c1 = 9.1~9.30, c2 = 32~34, c3 = 87~95, and d is in millimeters.

2. The air outlet structure of the air circulator according to claim 1, characterized in that: Each heat exchange wire (2) is bent to form an undulating structure; each heat exchange wire (2) is connected to the air outlet (1) through one side (201) of its respective undulating direction.

3. The air outlet structure of the air circulator according to claim 2, characterized in that: Each heat exchange wire (2) is sinusoidal in shape. For a single heat exchange wire (2), the heat exchange wire (2) forms a first arc segment (21) at the crest and a second arc segment (22) at the trough. For adjacent first arc segments (21) and second arc segments (22) on the heat exchange wire (2), the height difference between the centers of the first arc segment (21) and the second arc segment (22) is h1, and half the wavelength of the sine wave is w. Wherein, h1 = (1.2-1.5) * w, and the units of h1 and w are both millimeters.

4. The air outlet structure of the air circulator according to any one of claims 1-3, characterized in that: The air intake structure includes a heat exchange cavity (101) disposed on the air outlet (1). The air intake structure introduces heat exchange gas through the heat exchange cavity (101). The heat exchange cavity (101) also has an air outlet (103). Each heat exchange wire (2) is located inside the heat exchange cavity (101), and each heat exchange wire (2) is connected to the cavity wall of the heat exchange cavity (101) so as to be connected to the air outlet (1) through the cavity wall of the heat exchange cavity (101).

5. The air outlet structure of the air circulator according to claim 4, characterized in that: The heat exchange chamber (101) has an air inlet (102) through which the heat exchange gas is introduced; the heat exchange chamber (101) has a first chamber wall (1011) and a second chamber wall (1012) opposite to each other, and the air inlet (102) is disposed on the first chamber wall (1011); wherein, when each heat exchange wire (2) is bent to form an undulating structure, each heat exchange wire (2) is disposed on the second chamber wall (1012) through one side (201) of its respective undulating direction, and the other side (202) of the undulating direction of each heat exchange wire protrudes from the second chamber wall (1012).

6. The air outlet structure of the air circulator according to claim 4, characterized in that: The heat exchange cavity (101) is an annular cavity disposed within the wall thickness of the air outlet (1), and the annular cavity is disposed around the center line of the turbine air outlet passage (100); each of the heat exchange wires (2) is annular and is sleeved on the annular cavity wall.

7. The air outlet structure of the air circulator according to any one of claims 1-3 and 5-6, characterized in that: The air intake structure includes an air intake pipe (4), through which heat exchange gas is introduced.

8. The air outlet structure of the air circulator according to claim 7, characterized in that: The air intake pipe (4) includes a first pipe section (41) and a second pipe section (42) connected to each other. The air intake pipe (4) is disposed on the air outlet (1). The air intake pipe (4) introduces heat exchange gas from the outside through the end of the first pipe section (41) away from the second pipe section (42), and the air intake pipe (4) guides the introduced heat exchange gas to each of the heat exchange wires (2) through the end of the second pipe section (42) away from the first pipe section (41). The first pipe section (41) and the second pipe section (42) are connected by an arc-shaped pipe section (43), wherein the radius of the arc-shaped pipe section (43) is R, the inner hole of the air intake pipe (4) is a circular hole, and the diameter of the circular hole is D, wherein R = 16~18 mm and D = 8~9.5 mm.

9. The air outlet structure of the air circulator according to claim 7, characterized in that: When the air intake structure includes a heat exchange cavity (101) disposed on the air outlet (1), and each of the heat exchange wires (2) is located within the heat exchange cavity (101), each of the heat exchange wires (2) is formed into an undulating structure by bending, each of the heat exchange wires (2) is connected to the cavity wall of the heat exchange cavity (101) through one side (201) of its respective undulating direction, and the other side (202) of the undulating direction of each heat exchange wire protrudes from the cavity wall, the air intake structure... The gas structure introduces heat exchange gas into the heat exchange chamber (101) through the gas inlet pipe (4), so that the heat exchange chamber (101) introduces heat exchange gas through the gas inlet pipe (4); the other side (202) of the undulation direction of each heat exchange wire protrudes beyond the height h2 of the cavity wall, the distance between two adjacent heat exchange wires (2) is S, and the number of heat exchange wires (2) is N; the inner hole of the gas inlet pipe (4) is a circular hole, and the diameter of the circular hole is D; wherein, h2 The units for h2, S, and D are all millimeters.

10. An air circulator, characterized in that: The air outlet structure of the air circulator included in any one of claims 1-9.

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