An oxygen generator

Abstract

This application discloses an oxygen concentrator, including an outer shell and an inner shell. The inner shell forms a accommodating cavity, which includes a mutually separated air inlet cavity and an air outlet cavity. A compressor and a cooling fan are disposed within the air inlet cavity. The cooling fan has an air intake and an air outlet. The oxygen concentrator also includes an air inlet duct and an air outlet duct. The air inlet duct has an air outlet communicating with the air inlet cavity. The air intake and air outlet are located on opposite sides of the compressor and both face the compressor. The air outlet communicates with the air outlet duct through the air outlet cavity. This application constructs a directional airflow path from one side of the compressor to the air intake on the other side. Under the negative pressure of the cooling fan's air intake, the cooling air flows from one side of the compressor to the opposite side, achieving comprehensive coverage and uniform scouring of all surfaces in the circumferential direction of the compressor. This allows as much airflow as possible to contact the compressor and participate in heat exchange, greatly improving airflow utilization and cooling efficiency.

Description

Technical Field

[0001] This application belongs to the field of medical device technology, specifically relating to an oxygen generator. Background Technology

[0002] Oxygen concentrators are commonly used health devices in homes and medical settings, and their core air source is provided by a compressor. The compressor generates a significant amount of heat during operation; insufficient heat dissipation will significantly shorten the compressor's lifespan.

[0003] Existing oxygen concentrator cooling solutions generally employ forced air cooling via fans. External cooling air enters the compressor housing through the inlet, flows over the compressor surface for heat exchange, and is then exhausted through the exhaust vent. However, by directly blowing air onto the compressor surface to remove heat, the airflow is somewhat haphazard after contact with the compressor, failing to achieve effective full contact. Furthermore, the placement of the inlet and exhaust vents determines the overall airflow direction within the compressor housing. This housing is typically a large space, resulting in turbulent airflow that makes it difficult to ensure effective contact and cooling of the compressor. In some cases, cooling air may enter the housing but not fully flow over the compressor surface before being exhausted, resulting in airflow short-circuiting. A large amount of cooling air is wasted without effective heat exchange, and the compressor's main heat-generating components are not adequately cooled, leading to poor heat dissipation efficiency.

[0004] In addition, in order to achieve gas exchange between the inside and outside, the cavity housing the compressor usually needs to have an air inlet and / or an air outlet, and the fan is placed outside the cavity. This arrangement increases the distance between the fan and the compressor, further reducing the air force of the fan acting on the compressor surface. On the other hand, the mechanical vibration noise and airflow pulsation noise of the compressor during operation will be directly radiated outward through these openings, resulting in a lot of noise during the operation of the oxygen concentrator, which seriously affects the user experience.

[0005] Therefore, existing oxygen concentrator heat dissipation technologies cannot simultaneously achieve efficient cooling of the compressor and low-noise operation of the oxygen concentrator. Summary of the Invention

[0006] This application provides an oxygen concentrator to solve the problems of poor heat dissipation of the compressor in existing oxygen concentrators and the large noise that accompanies the heat dissipation process of oxygen concentrators.

[0007] The technical solution adopted in this application is as follows: An oxygen concentrator includes an outer shell and an inner shell disposed inside the outer shell. The inner shell forms a receiving cavity, which includes a mutually separated air inlet cavity and an air outlet cavity. A compressor and a cooling fan are disposed in the air inlet cavity, and the cooling fan has an air intake and an air outlet. The oxygen concentrator also includes an air inlet duct and an air outlet duct. The air inlet duct has an air outlet communicating with the air inlet cavity. The air intake and air outlet are located on opposite sides of the compressor and are both oriented towards the compressor. The air outlet communicates with the air outlet duct through the air outlet cavity.

[0008] The compressor is a piston compressor, which includes a cylinder block and a cylinder liner protruding from the surface of the cylinder block. The cooling fan is set to correspond to the cylinder liner, and the air intake is set to face the cylinder liner.

[0009] The cylinder liner protrudes upward from the top of the cylinder block. The cooling fan is located above the cylinder liner, the air intake is located at the bottom of the cooling fan and faces the cylinder liner, and the air outlet is located on the bottom wall of the air intake chamber and faces upward.

[0010] The bottom wall of the air inlet cavity is provided with a mating groove that matches the shape of the bottom of the cylinder body. At least part of the cylinder body is accommodated in the mating groove, and the airflow outlet is located in the mating groove.

[0011] The oxygen concentrator also includes an air guide, which is installed around a portion of the compressor to form an air intake channel that connects to the air inlet. There is an air intake gap between the air guide and the outer wall of the compressor.

[0012] The suction duct has an inlet side fitted outside the compressor and an outlet side connected to the suction port. The suction duct is equipped with guide vanes arranged in a spiral shape from the inlet side to the outlet side to form a spiral air duct within the suction duct.

[0013] The outer shell is equipped with an air inlet, and an air intake space is formed between the outer shell and the inner shell. The inner shell is a closed structure, and the air intake cavity is connected to the air intake space through the air intake duct.

[0014] The outer shell is provided with an air inlet, and an air intake space is formed between the outer shell and the inner shell. The air intake duct has an airflow inlet, which is located opposite to the air inlet on both sides of the inner shell. At least one heating element is provided between the air inlet and the airflow inlet.

[0015] The heating components include an adsorption tower assembly, a control board, and a main control valve. The adsorption tower assembly and the inner shell are arranged side by side, and the upper edge of the adsorption tower assembly is higher than the inner shell to form an installation space above the inner shell. The control board and the main control valve are located in the installation space.

[0016] The oxygen concentrator also includes a partition set in the accommodating cavity, with the exhaust cavity located inside the partition; or the partition and the inner shell cooperate to form an exhaust cavity.

[0017] The oxygen concentrator also includes a base assembly located below the inner shell. The air inlet duct and the air outlet duct are both located inside the base assembly. The inner shell and the base assembly cooperate to form a receiving cavity. The base assembly is provided with an exhaust port that communicates with the exhaust duct, and the outer shell or the base assembly is provided with an air inlet that communicates with the air inlet duct.

[0018] The base assembly includes a bottom shell and at least one partition. The bottom shell and the partition form an air duct cavity with at least two layers of air duct space in the vertical direction. Both the air inlet duct and the air outlet duct are located in the air duct cavity. The air inlet duct and the air outlet duct are isolated from each other, and at least one of them is formed by air duct spaces located in different layers.

[0019] The partition includes a first partition and a second partition located above the first partition. The first partition and the bottom wall of the bottom shell cooperate to form a lower air duct space. The first partition and the second partition form an upper air duct space. The air inlet duct is connected to the air inlet cavity through a first air outlet provided on the first partition and an air outlet provided on the second partition. The air outlet duct connects the air outlet cavity and the air outlet through a second air outlet provided on the first partition and a third air outlet provided on the second partition.

[0020] The first air inlet and the air outlet are staggered vertically, and / or the second air inlet and the third air inlet are staggered vertically.

[0021] The air inlet duct includes a first air inlet section located in the lower air duct space and a second air inlet section located in the upper air duct space. The second air inlet section includes a first branch section and a second branch section that are separated from each other and connected to the first air inlet section respectively. There are two sets of air outlets, which are respectively set to correspond to the first branch section and the second branch section. The horizontal projections of the two sets of air outlets are located at different positions of the compressor.

[0022] The base assembly is equipped with a limiting structure for limiting the foot position of the compressor.

[0023] Due to the adoption of the above technical solution, the beneficial effects achieved by this application are as follows: This application divides the original large-volume housing into two independent chambers: an air inlet chamber and an air outlet chamber. The compressor and cooling fan are both located in the air inlet chamber, placing them in the same space. The cooling fan can be arranged adjacent to the compressor, significantly reducing the distance between them. The suction negative pressure generated by the cooling fan during operation can act directly on the compressor surface with minimal friction loss. At the same fan speed, the actual air velocity on the compressor surface is significantly increased, or the fan can operate at a lower speed to achieve the same cooling effect, thereby reducing the power consumption of the cooling fan. At the same time, since the compressor and cooling fan are located in the same air inlet chamber, there is no need to open any openings on the inner shell for direct airflow. The mechanical vibration noise and airflow pulsation noise of the compressor during operation are completely confined inside the inner shell and cannot be directly radiated outward through openings. Air intake and exhaust are achieved through independent air intake and exhaust ducts. The reflection, absorption, and interference of sound waves by the duct walls further attenuate the transmitted noise, establishing multiple sound barriers between the noise source and the external environment.

[0024] Furthermore, this application places the airflow outlet of the air inlet duct and the air intake of the cooling fan on opposite sides of the compressor, both facing the compressor. This creates a directional airflow path that runs from one side of the compressor, across its surface, to the air intake on the other side. After the cooling air enters the air inlet chamber from the airflow outlet, it must flow from one side of the compressor to the opposite side under the negative pressure of the cooling fan's air intake before it can be drawn in by the cooling fan. This forced path allows the cooling air to flow through the compressor from one side to the other, achieving comprehensive coverage and uniform flushing of all surfaces in the circumferential direction of the compressor. This eliminates the airflow short-circuiting phenomenon, allowing as much airflow as possible to contact the compressor and participate in heat exchange, greatly improving airflow utilization and cooling efficiency. Attached Figure Description

[0025] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, illustrate exemplary embodiments and are used to explain this application, but do not constitute an undue limitation of this application. In the drawings: Figure 1 This is a schematic diagram of an oxygen generator according to one embodiment of this application; Figure 2 This is a schematic diagram of an oxygen generator according to one embodiment of this application, wherein the outer casing is not shown; Figure 3 This is a schematic diagram of an oxygen generator according to one embodiment of the present application, wherein the outer shell and inner shell are not shown; Figure 4 This is an exploded view of a portion of the oxygen generator structure according to one embodiment of this application; Figure 5 This is a schematic diagram of the compressor and cooling fan according to one embodiment of this application; Figure 6 This is a schematic diagram of the internal structure of the air guide component according to one embodiment of this application; Figure 7 This is an exploded view of the structure of a cooling fan and air guide component according to one embodiment of this application; Figure 8 This is a schematic diagram of the base assembly according to one embodiment of this application; Figure 9 for Figure 8 Exploded view of the structure of the base assembly; Figure 10 This is a schematic diagram of the bottom shell structure according to one embodiment of this application; Figure 11 This is a schematic diagram of the structure of the first partition in one embodiment of this application; Figure 12 This is a schematic diagram of the structure of the second partition in one embodiment of this application; Figure 13 This is a schematic diagram of the compressor according to one embodiment of this application; Figure 14 This is a schematic diagram of the structure of the limiting member according to one embodiment of this application; Figure 15 This is a schematic diagram of the assembly of the compressor and base assembly according to one embodiment of this application.

[0026] in: 1. Outer casing; 11. Air inlet; 12. Air inlet space; 13. Adsorption tower assembly; 14. Main control valve; 15. Control panel; 16. Installation space; 2 Inner shell; 21 Receptacle cavity; 22 Air inlet cavity; 23 Air outlet cavity; 3. Compressor; 31. Cylinder block; 32. Cylinder liner; 33. Base; 4. Base assembly; 41. Bottom shell; 411. Exhaust vent; 412. First mating cavity; 413. Second mating cavity; 42. First partition; 421. First air vent; 422. Second air vent; 43. Second partition; 431. Third air vent; 44. Mating groove; 45. Limiting component; 451. Limiting space; 452. Limiting side wall; 453. Limiting top wall; 46. Support platform; 5. Air inlet duct; 51. Airflow inlet; 52. Airflow outlet; 53. First air inlet section; 54. Second air inlet section; 541. First diversion section; 542. Second diversion section; 6-row air duct; 61 First air duct section; 62 Second air duct section; 7 Cooling fan; 71 Air intake; 72 Air exhaust; 8. Air guide; 81. Air intake duct; 82. Inlet side; 83. Outlet side; 84. Guide vanes; 85. Spiral air duct; 86. Connecting parts; 9. Separator; 91. Raised portion. Detailed Implementation

[0027] To more clearly illustrate the overall concept of this application, a detailed explanation is provided below with reference to the accompanying drawings.

[0028] Many specific details are set forth in the following description in order to provide a full understanding of this application. However, this application may also be implemented in other ways different from those described herein. Therefore, the scope of protection of this application is not limited to the specific embodiments disclosed below.

[0029] Furthermore, it should be understood in the description of this application that the terms "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and are not intended to 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 of the present invention.

[0030] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a communication connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0031] In this application, unless otherwise expressly specified and limited, the "above" or "below" of the second feature can mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium. In the description of this specification, references to terms such as "implementation," "example," "a particular embodiment," "example," or "specific example," etc., indicate that the specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described can be combined in any suitable manner in one or more embodiments or examples.

[0032] like Figures 1 to 4 , Figure 9As shown, an oxygen concentrator includes an outer shell 1 and an inner shell 2 placed inside the outer shell 1. The inner shell 2 forms a receiving cavity 21, which includes an air inlet cavity 22 and an air outlet cavity 23 separated from each other. A compressor 3 and a cooling fan 7 are disposed in the air inlet cavity 22. The cooling fan 7 has an air intake 71 and an air outlet 72. The oxygen concentrator also includes an air inlet duct 5 and an air outlet 6. The air inlet duct 5 has an air outlet 52 communicating with the air inlet cavity 22. The air intake 71 and the air outlet 52 are located on opposite sides of the compressor 3 and are both oriented towards the compressor 3. The air outlet 72 is connected to the air outlet duct 6 through the air outlet cavity 23.

[0033] This application divides the original large-volume accommodating cavity 21 into two independent chambers: an air inlet chamber 22 and an air outlet chamber 23. The compressor 3 and the cooling fan 7 are both located in the air inlet chamber 22, placing them in the same space. In this way, the cooling fan 7 can be arranged close to the compressor 3, significantly shortening the distance between them. The suction negative pressure generated by the cooling fan 7 during operation can act directly on the surface of the compressor 3 with minimal friction loss. Under the same fan speed, the actual air velocity on the surface of the compressor 3 is significantly increased, or the fan can operate at a lower speed under the premise of achieving the same heat dissipation effect, thereby reducing the power consumption of the cooling fan 7. On the other hand, since the compressor 3 and the cooling fan 7 are both located in the air inlet cavity 22, there is no need to open any openings on the inner shell 2 for direct airflow. The mechanical vibration noise and airflow pulsation noise of the compressor 3 during operation are completely confined inside the inner shell 2 and cannot be directly radiated outward through the openings. The air inlet and exhaust are achieved through independent air inlet ducts 5 and exhaust ducts 6. The reflection, absorption and interference of sound waves by the duct walls further attenuate the transmitted noise, thus establishing multiple sound barriers between the noise source and the external environment.

[0034] Meanwhile, unlike existing fan-driven direct airflow mode for compressor 3, this solution employs a suction method, placing compressor 3 in the suction path of cooling fan 7. The negative pressure zone created by the fan at the suction port 71 actively guides external cooling air across the surface of compressor 3. Because the suction port 71 faces compressor 3 directly, the air surrounding compressor 3 is continuously drawn away, creating a localized low-pressure zone. This clearly defines the airflow path in space, ensuring that the cooling airflow passes over compressor 3 as much as possible. Furthermore, the suction-type cooling system ensures that each intake of cooling air is fresh, cool air from outside compressor 3, preventing the gradual decrease in cooling efficiency caused by repeated circulation of hot air within the compressor 3's chamber.

[0035] Furthermore, this application places the air outlet 52 of the air inlet duct 5 and the air intake 71 of the cooling fan 7 on opposite sides of the compressor 3, both facing the compressor 3. This creates a directional airflow path that passes through the surface of the compressor 3 from one side to the air intake 71 on the other side. After the cooling air enters the air inlet chamber 22 from the air outlet 52, it must flow from one side of the compressor 3 to the opposite side under the negative pressure of the air intake 71 of the cooling fan 7 before it can be sucked in by the cooling fan 7. This forced path makes the cooling air flow through the outer surface of the compressor 3 from one side to the other, achieving full coverage and uniform flushing of all surfaces of the compressor 3 in the circumferential direction, eliminating the airflow short-circuiting phenomenon, and allowing as much airflow as possible to contact the compressor 3 to participate in heat exchange, greatly improving the airflow utilization rate and cooling efficiency.

[0036] It should be noted that this application does not limit the specific arrangement of the air intake 71 and the air outlet 52. In one embodiment, the air intake 71 and the air outlet 52 are arranged facing each other. For example, the air intake 71 is located directly above the compressor 3, and the air outlet 52 is located directly below the compressor 3. In another embodiment, the air intake 71 and the air outlet 52 can simply be located on opposite sides of the compressor 3. For example, the air intake 71 can be located to the left of the compressor 3 (it can be directly left, upper left, or lower left), and the air outlet 52 can be located to the right of the compressor 3 (it can be directly right, upper right, or lower right).

[0037] The hot air discharged from the outlet 72 of the cooling fan 7 is directly sent into the exhaust chamber 23 and discharged through the exhaust duct 6. First, the hot air cannot flow back into the intake chamber 22 to mix with the cooling airflow, eliminating the stagnation and secondary circulation of hot air in the chamber, ensuring that the compressor 3 in the intake chamber 22 is always surrounded by fresh, low-temperature cooling air. Second, the hot airflow blown out from the outlet 72 passes through the exhaust chamber 23 and the exhaust duct 6 in sequence and is directly discharged to the outside. All heat-generating components involved in cooling are located on the intake path of the cooling fan 7, and heat dissipation is completed by the intake airflow. No heat-generating components are placed on the blowing path of the cooling fan 7, avoiding the problem of violent collision between the airflow pressurized and accelerated by the cooling fan 7 and the heat-generating components, which would generate turbulence and produce a lot of noise.

[0038] Preferably, such as Figure 1 , Figure 2 As shown, the outer shell 1 is provided with an air inlet 11, and an air intake space 12 is formed between the outer shell 1 and the inner shell 2. The inner shell 2 is a closed structure, and the air intake cavity 22 is connected to the air intake space 12 through the air intake duct 5.

[0039] The inner shell 2 is a closed structure, meaning there are no openings on the wall of the inner shell 2 for direct airflow. All airflow entering and exiting the inner shell 2 is completed through the air intake duct 5 and the air exhaust duct 6. The noise of the compressor 3 and the cooling fan 7 is completely confined inside the inner shell 2 and cannot be directly radiated outward through the openings on the wall of the inner shell 2.

[0040] Specifically, such as Figure 2 As shown, the inner shell 2 includes multiple wall panels, which are fixed together by welding, riveting, or other methods to form a complete inner shell 2. The inner shell 2 can be disassembled into multiple wall panels of different sizes and shapes, and can be flexibly assembled into different shapes and sizes according to needs and the external dimensions of the compressor 3. Of course, the inner shell 2 can also be a one-piece structure, so that the size and shape of the accommodating cavity 21 are fixed, which is not limited here.

[0041] As a preferred embodiment of this application, such as Figures 3 to 5 As shown, the compressor 3 is a piston compressor 3. The compressor 3 includes a cylinder body 31 and a cylinder liner 32 protruding from the surface of the cylinder body 31. The cooling fan 7 is correspondingly arranged with the cylinder liner 32, and the air intake 71 is arranged facing the cylinder liner 32.

[0042] Cylinder liner 32 is the area where heat is most concentrated in compressor 3, and the surface temperature of cylinder liner 32 directly determines the gas temperature at the end of compression. If the heat from cylinder liner 32 cannot be dissipated in time, the reliability of compressor 3 will decrease. Therefore, heat dissipation of the cylinder liner 32 area of ​​compressor 3 is particularly important.

[0043] The air intake 71 is positioned towards the cylinder liner 32, so that under the negative pressure of the air intake 71, the cooling airflow is forced to converge and flow from all sides of the cylinder liner 32 towards the air intake 71, and the outer wall of the cylinder liner 32 is uniformly scourned by airflow in all directions. In addition, since the cylinder liner 32 protrudes from the surface of the cylinder body 31, there is no obstruction from the cylinder body 31 itself between it and the air intake 71, minimizing the obstruction in the airflow path, so that the cooling fan 7 can obtain the maximum airflow speed on the surface of the cylinder liner 32 with the lowest suction resistance at the same speed.

[0044] Understandably, since the air intake 71 is positioned towards the cylinder liner 32, the air outlet 52 is positioned on the opposite side towards the cylinder block 31. Therefore, after the cooling air enters the air intake chamber 22 from the air outlet 52, it first contacts the relatively cool surface of the cylinder block 31. After flowing over and cooling the surface of the cylinder block 31, it flows upward along the surface of the cylinder block 31 to the area of ​​the cylinder liner 32 where heat is more intense, and is finally drawn in by the air intake 71. This sequential cooling of the compressor 3, first the cylinder block 31 and then the cylinder liner 32, allows the same cooling air to efficiently cool the cylinder block 31 and the cylinder liner 32 at different temperature ranges. When the cooling air first exchanges heat with the cylinder block 31, its temperature is still at its lowest, allowing it to efficiently remove heat from the surface of the cylinder block 31 with the greatest temperature difference. At this point, although the airflow temperature rises, it is still far lower than the cylinder liner 32 temperature. Subsequently, when the airflow flows through the cylinder liner 32, it can still maintain a sufficient temperature difference for efficient heat exchange. This gradient cooling method makes the temperature change of the cylinder liner 32 more gradual, reducing the risk of thermal shock damage.

[0045] In a preferred embodiment, such as Figures 3 to 5 As shown, the cooling fan 7 is a centrifugal fan, meaning its air intake 71 is located on the end face and its air outlet 72 is located on its circumferential surface, with the air intake 71 and air outlet 72 oriented perpendicularly to each other. This allows the axis of the cooling fan 7 to be arranged parallel to the cylinder liner 32, reducing the space occupied by the cooling fan 7 in the height direction and achieving miniaturization.

[0046] Preferably, such as Figure 3 , Figure 5 As shown, the axis of the cooling fan 7 coincides with the axis of the cylinder liner 32, so that the center of the negative pressure area generated by the cooling fan 7 when it is working is exactly aligned with the axial center line of the cylinder liner 32. The airflow around the cylinder liner 32 is evenly drawn into the air intake 71, and there will be no uneven heat dissipation phenomenon caused by the offset of the air intake 71, where the airflow velocity is fast on one side of the cylinder liner 32 and slow on the other side. The coaxial arrangement ensures uniform suction on the entire circumferential surface of the cylinder liner 32, so that the high temperature heat energy in all directions of the cylinder liner 32 is evenly removed.

[0047] Of course, in other embodiments, the air intake 71 can also be arranged at other positions on the cylinder liner 32. For example, the axis of the air intake 71 can be parallel to but not coincident with the axis of the cylinder liner 32, that is, the two are arranged eccentrically. Or, the air intake 71 can also be located on one side of the cylinder liner 32, that is, the axis of the air intake 71 is set at an angle or perpendicular to the axis of the cylinder liner 32.

[0048] Furthermore, such as Figures 3 to 5 As shown, the cylinder liner 32 protrudes upward from the top of the cylinder body 31, the cooling fan 7 is located above the cylinder liner 32, the air intake 71 is located at the bottom of the cooling fan 7 facing the cylinder liner 32, and the air outlet 52 is located on the bottom wall of the air intake cavity 22 and faces upward.

[0049] This embodiment constructs a complete airflow path that runs from bottom to top through the compressor 3. Since the air outlet 52 is set upward on the bottom wall of the air inlet chamber 22, and the air inlet 71 is set downward on the top of the compressor 3 (the cooling fan 7 is located above the compressor 3, and the air inlet 71 is set on the lower end face of the cooling fan 7), the two form a directional suction from bottom to top in the vertical direction. After the cooling air is ejected upward from the air outlet 52 at the bottom of the compressor 3, it is drawn upward from the bottom of the compressor 3 by the negative pressure of the air inlet 71 facing downward before reaching the air inlet 71 at the top. This path forces the cooling air to flow fully from the bottom to the top along the entire axial length of the compressor 3, especially the cylinder liner 32, avoiding the problem that the airflow only washes over a local area of ​​the compressor 3 while other areas are not cooled.

[0050] In actual use, since the air outlet 52 is located on the bottom wall of the air inlet chamber 22, the direction of gravity of the compressor 3 is opposite to the direction of airflow. The cooling air ejected from the air outlet 52 is blocked by the compressor body and diffuses to the surroundings and rises along the outer wall of the cylinder liner 32. This diffusion process maximizes the contact area between the airflow and the bottom of the compressor 3, so that the compressor 3 can be fully wrapped from all sides during the upward flow of the airflow.

[0051] It should be noted that this application does not limit the number of cylinder liners 32 and cooling fans 7. In a preferred embodiment, such as Figures 3 to 5 As shown, there are multiple cylinder liners 32, which are located on the top of the cylinder block 31 and extend upward. The cooling fan 7 is located above the cylinder liners 32 and is arranged in a one-to-one correspondence with the cylinder liners 32.

[0052] For a dual-cylinder or multi-cylinder compressor 3, multiple cylinder liners 32 alternately perform compression and intake strokes during operation, resulting in a phase difference in their heat load distribution. By using multiple cooling fans 7, each independently corresponding to one cylinder liner 32 for suction and cooling, each cylinder liner 32 can receive an independent supply of cool air, avoiding the airflow interference that occurs when a single fan simultaneously draws air from multiple cylinder liners 32. Furthermore, the cooling fans 7 are positioned above the cylinder liners 32, utilizing the buoyancy effect of the naturally rising hot air. Since the direction of the upward suction is aligned with the direction of the cooling fans 7, only a small driving force is needed to overcome the flow resistance. From an assembly and maintenance perspective, the cooling fans 7 are arranged one-to-one with the cylinder liners 32 and independently installed on top of the compressor 3. If one cooling fan 7 fails, only that cooling fan 7 needs to be replaced without disassembling the others, significantly improving maintenance convenience.

[0053] For example, such as Figures 3 to 5 As shown, there are two cylinder liners 32, therefore, there are also two cooling fans 7, which are set one-to-one with the cylinder liners 32.

[0054] In another embodiment, there is one cooling fan 7. That is, when there are multiple cylinder liners 32, one cooling fan 7 is set for multiple cylinder liners 32. Specifically, the cooling fan 7 can be arranged at the center of the cylinder liner 32 group formed by multiple cylinder liners 32, so that the intake airflow passes through the surface of multiple cylinder liners 32 at the same time and reaches the air intake 71 of the cooling fan 7.

[0055] It should be noted that this application does not limit the fixing method of the cooling fan 7. In one embodiment, a mounting bracket for fixing the compressor 3 is provided in the air inlet cavity 22, and the cooling fan 7 is fixed to the mounting bracket so that the cooling fan 7 and the compressor 3 are assembled into a single component through the mounting bracket. On the one hand, the two can be pre-assembled and then installed together in the air inlet cavity 22, reducing assembly difficulty and improving assembly efficiency. On the other hand, it can also ensure that the relative position of the cooling fan 7 and the cylinder liner 32 is fixed, avoiding the impact of assembly errors on the cooling efficiency of the compressor 3. In another embodiment, the cooling fan 7 is installed independently of the compressor 3 in the air inlet cavity 22. Specifically, it can be fixed to the shell wall of the inner shell 2 through a fixing structure on the cooling fan 7, or the cooling fan 7 can be fixed in the air inlet cavity 22 through an independent fan bracket.

[0056] Preferably, such as Figure 3 , Figure 8 As shown, the bottom wall of the air inlet cavity 22 is provided with a mating groove 44 that matches the bottom shape of the cylinder body 31. At least a portion of the cylinder body 31 is accommodated in the mating groove 44, and the air outlet 52 is disposed in the mating groove 44.

[0057] The groove 44 forms a partially surrounding limiting structure around the bottom of the cylinder 31 in space. During the assembly of the whole machine, the compressor 3 can be accurately positioned in the design position without additional tooling or fixtures, which greatly simplifies the assembly process and improves the assembly consistency.

[0058] Because the air outlet 52 is located inside the mating groove 44, the cooling air delivered from the air inlet duct 5 is ejected from the air outlet 52 and directly impacts the bottom surface of the cylinder 31 within the narrow space confined by the groove. This avoids the expansion loss and velocity attenuation caused by the sudden expansion of the space after the airflow enters the air inlet cavity 22. The groove structure, by confining the airflow diffusion space, allows the high-speed airflow to act directly on the bottom of the cylinder 31, ensuring that the airflow contacts the bottom of the compressor 3 at a relatively high speed and flows upward along the surface of the compressor 3. Moreover, the gap formed between the mating groove 44 and the outer surface of the bottom of the cylinder 31 restricts the airflow, better enveloping the cylinder 31, thereby improving the contact effect between the airflow and the cylinder 31 and increasing the heat exchange efficiency. The cooling air ejected from the air outlet 52 flows over the bottom surface of the cylinder 31 at a high speed within this gap, forming a high-speed airflow layer similar to an air film, which enhances the heat dissipation of the bottom of the cylinder 31.

[0059] Specifically, such as Figure 3 , Figure 5 , Figure 8 As shown, the cylinder body 31 is a cylindrical structure with a horizontal axis, and its bottom surface is an arc surface. The groove 44 is an arc-shaped groove that matches its shape, and the airflow outlet 52 is opened on the arc surface.

[0060] It should be noted that this application does not limit the formation of the air inlet cavity 22 and the air outlet cavity 23. In one embodiment, the space inside the accommodating cavity 21 is divided by various functional components provided in the accommodating cavity 21. For example, the accommodating cavity 21 is divided into the air inlet cavity 22 and the air outlet cavity 23 by the cooperation of the compressor 3 and the cooling fan 7, so that the air intake 71 of the cooling fan 7 is connected to the air inlet cavity 22 and the air outlet 72 is connected to the air outlet cavity 23.

[0061] In another implementation, such as Figure 3 , Figure 4 As shown, by providing a separate partition 9 inside the accommodating cavity 21, the accommodating cavity 21 is divided into an air inlet cavity 22 and an air outlet cavity 23.

[0062] Specifically, in a preferred embodiment, the partition 9 is independently formed within the accommodating cavity 21 to create an exhaust cavity 23 that communicates with the air outlet 72, so that the airflow of the cooling fan 7 enters the exhaust channel through the exhaust cavity 23. For example, the partition 9 is a tubular structure that connects the air outlet 72 to the exhaust channel, while the space outside the accommodating cavity 21 forms an air inlet cavity 22.

[0063] In another preferred embodiment, such as Figure 3 , Figure 4 As shown, the partition 9 is disposed within the accommodating cavity 21, and forms an exhaust cavity 23 by cooperating with the inner shell 2 and / or the cooling fan 7. Specifically, as... Figure 3 , Figure 4 As shown, the partition 9 has a mating portion that connects with the air outlet 72 of the cooling fan 7, and a fitting portion that extends laterally away from the cooling fan 7. The fitting portion fits with the side wall of the inner shell 2 to form an exhaust cavity 23. Furthermore, the partition 9 also has a raised portion 91 that protrudes towards the interior of the exhaust cavity 23 to further reduce the volume of the exhaust cavity 23, while also increasing the volume of the air inlet cavity 22, thus avoiding interference with the compressor 3.

[0064] like Figure 3 As shown, the air inlet chamber 22 and the air outlet chamber 23 are arranged laterally (left and right) within the accommodating chamber 21.

[0065] Furthermore, the separator 9 can be fixed to the inner shell 2 by means of screws, rivets, clips, etc.

[0066] As a preferred embodiment of this application, such as Figures 3 to 5 As shown, the oxygen concentrator also includes an air guide 8, which covers a portion of the compressor 3 to form an air intake channel 81 that connects to the air intake 71. There is an air intake gap between the air guide 8 and the outer wall of the compressor 3 (not shown in the figure).

[0067] Before entering the air intake 71, the cooling airflow must pass through the air inlet gap between the air guide 8 and the compressor 3. The existence of this gap significantly reduces the cross-sectional area of ​​the gas flow, which leads to an increase in flow velocity. When the high-speed airflow brushes against the outer wall surface of the compressor 3, it can effectively break the thermal boundary layer at the wall surface of the compressor 3, allowing the heat of the compressor 3 to be quickly carried away by the high-speed airflow, significantly improving the surface convective heat transfer coefficient.

[0068] Specifically, to achieve better coverage of a portion of the compressor 3 by the air guide 8 and to make the air intake gap between them more uniform, the shapes of the air guide 8 and a portion of the compressor 3 can be designed to mimic their contours. In a preferred embodiment, since the cylinder liner 32 experiences significant heat generation, the air guide 8 is positioned around the outer periphery of the cylinder liner 32, such as... Figures 3 to 5 As shown, since the cylinder liner 32 has a cylindrical structure, the cross-section of the air guide 8 is also circular, so that the air intake gap formed between it and the outer wall of the cylinder liner 32 is more uniform in the circumferential direction.

[0069] In this embodiment, the air guide 8 surrounds at least part of the compressor 3, and the air inlet gap serves as the only inlet of the air intake channel 81. This forces each stream of air participating in cooling to pass through the surface of the cylinder block 31 and reach the cylinder liner 32 before it can be drawn into the cooling fan 7 through the air intake channel 81.

[0070] Specifically, such as Figure 3 , Figure 5 As shown, in one embodiment, a portion of the cylinder liner 32 in the axial direction (the end closer to the cooling fan 7) is covered by the air guide 8, while another portion (the end farther from the cooling fan 7) is exposed outside the air guide 8. Of course, the air guide 8 can also completely cover the cylinder liner 32 in the axial direction, which is not limited here.

[0071] Furthermore, such as Figure 6 As shown, the suction channel 81 has an inlet side 82 sleeved on the outside of the compressor 3 and an outlet side 83 connected to the suction port 71. The suction channel 81 is provided with guide vanes 84 arranged in a spiral shape from the inlet side 82 to the outlet side 83 to form a spiral air duct 85 in the suction channel 81.

[0072] When the cooling airflow enters the suction channel 81 through the air inlet gap, under the forced guidance of the spiral guide vanes 84, the airflow no longer moves in a straight line along the axial direction, but transforms into a rotating airflow that spirals forward from the inlet side 82 to the outlet side 83. Compared with the axial straight-line flow, the residence time and contact path of the spiral airflow on the same circumference of the cylinder liner 32 are significantly increased. Every surface of the outer wall of the cylinder liner 32 is repeatedly swept by the rotating airflow, resulting in more thorough heat exchange. In addition, the spiral air duct 85 gives the airflow entering the suction port 71 of the radiator fan 7 a pre-rotation momentum. When the rotation direction of the airflow matches the rotation direction of the fan blades of the radiator fan 7, the flow loss at the inlet of the fan blades can be reduced, that is, a larger suction volume can be obtained under the same input power, thereby improving the suction efficiency of the radiator fan 7.

[0073] Preferably, such as Figure 6 As shown, the guide vane 84 is fixed to the inner wall of the suction channel 81. This makes the guide vane 84 and the air guide component 8 an integral structure. The fixed connection between the vane root and the wall surface can withstand the bending moment and torque applied by the airflow during high-speed rotation and scouring, ensuring that the vane does not experience vibration fatigue fracture during long-term operation. During assembly, the integral fixing of the guide vane 84 and the suction channel 81 means that the entire air guide component 8 can be directly inserted and installed from above the cylinder liner 32, greatly simplifying the assembly process and avoiding the problem of misalignment of the spiral angle due to rotation or displacement of the vane position during assembly, thus ensuring consistent heat dissipation of the product.

[0074] Of course, in other embodiments, the guide vane 84 can also be fixed in other positions, as long as it is located in the suction channel 81. For example, the guide vane 84 can be set as an independent component and installed in the suction channel 81. Or, the guide vane 84 can be fixed to the outer wall of the cylinder liner 32. There are no limitations here.

[0075] Furthermore, such as Figure 6 As shown, there are multiple guide vanes 84 arranged at circumferential intervals along the cylinder liner 32 to form a spiral air duct 85 between two adjacent guide vanes 84.

[0076] Multiple guide vanes 84 are evenly distributed circumferentially, dividing the suction channel 81 into multiple parallel spiral sub-channels. Each sub-channel independently guides a portion of the airflow along the spiral path, thus homogenizing the airflow distribution circumferentially. Even if there is uneven air intake in the circumferential direction at the inlet gap 82 of the suction channel 81, the multiple guide vanes 84 can redistribute the airflow after it enters the suction channel 81. The airflow is guided by its respective spiral air ducts 85 to circumferentially bypass areas with insufficient air intake, ensuring that the entire circumferential surface of the cylinder liner 32 is covered by rotating airflow and avoiding localized heat dissipation dead zones. In addition, the increased number of vanes allows for a suitable reduction in the height of each vane, reducing airflow resistance while maintaining the guiding effect.

[0077] In another embodiment, the guide vane 84 may be a single vane that extends continuously in a spiral to form a continuous spiral duct 85.

[0078] In a preferred embodiment, the air guide 8 is a structure made of a flexible material, such as... Figure 7 As shown, the heat dissipation assembly also includes a connector 86, which is a rigid structure. The air guide 8 is fixedly connected to the cooling fan 7 through the connector 86.

[0079] When the oxygen concentrator is working, the compressor 3 itself has periodic vibrations. If the air guide 8 is made of a rigid structure and is directly rigidly connected to the cooling fan 7, the vibration of the compressor 3 will be directly transmitted to the fan through the air guide 8, which will accelerate bearing wear and increase vibration noise.

[0080] In this embodiment, the air guide 8 made of flexible material can effectively absorb and attenuate the mechanical vibration transmitted from the compressor 3 to the air guide 8, playing a role in vibration isolation and buffering, so that the operation of the cooling fan 7 is not disturbed by the vibration of the compressor 3, ensuring that the bearing works in a stable state and extending the service life of the cooling fan 7.

[0081] Meanwhile, there is an air intake gap between the air guide 8 and the outer wall of the cylinder liner 32. When the compressor 3 vibrates, the cylinder liner 32 may have a slight radial oscillation. The flexible air guide 8 has a certain elastic deformation capability when it contacts or approaches the cylinder liner 32. Even if the gap shrinks instantly due to vibration, it will not have a rigid collision with the cylinder liner 32 to produce abnormal noise or damage the surface of the cylinder liner 32.

[0082] During assembly, the air guide 8 is first combined with the rigid connector 86, and then fixedly connected to the fan through the connector 86. The positioning reference of the flexible air guide 8 is transferred to the rigid connector 86. The high dimensional stability of the rigid connector 86 ensures the coaxiality and spacing between the air guide 8 and the fan air intake 71, avoiding installation position deviation caused by the instability of the flexible material's own dimensions or deformation under stress during assembly.

[0083] Specifically, such as Figure 7 As shown, the air guide 8 can be made of materials such as silicone or rubber, and the connecting part 86 is a ring-shaped pressure plate. During assembly, the air guide 8 and the pressure plate are first combined and installed as a component, and then the air guide 8, the pressure plate and the cooling fan 7 are fixedly connected by one or more screws.

[0084] As a preferred embodiment of this application, such as Figure 1 , Figure 2 As shown, the outer shell 1 is provided with an air inlet 11, and an air inlet space 12 is formed between the outer shell 1 and the inner shell 2. The air inlet duct 5 has an airflow inlet 51, which is disposed opposite to the air inlet 11 on both sides of the inner shell 2. At least one heating element is disposed between the air inlet 11 and the airflow inlet 51.

[0085] After the external cooling air enters the air intake space 12 through the air inlet 11 of the outer shell 1, it flows sequentially over the surfaces of each heat-generating component arranged along the path, and then reaches the airflow inlet 51 of the air intake duct 5 before entering the interior of the inner shell 2. This arrangement allows the cooling air to fully exchange heat with each heat-generating component along a relatively long path within the air intake space 12, ensuring that the cooling air has already dissipated heat from each heat-generating component before entering the inner shell 2.

[0086] In the entire heat dissipation system of the oxygen generator, the same cooling air successively cools the heat-generating components (such as the adsorption tower assembly 13) in the air intake space 12 and the compressor 3 in the air intake cavity 22, forming a reasonable gradient heat dissipation sequence and maximizing the utilization value of the cooling air.

[0087] Specifically, after the external cooling air is drawn in through the air inlet 11 of the outer casing 1, it first flows through the air inlet space 12 to cool the heat-generating components, and then enters the air inlet cavity 22 through the air inlet duct 5. Under the suction of the cooling fan 7, it flows orderly over the surface of the compressor 3 for cooling, and finally is drawn in by the cooling fan 7 and discharged outside the machine through the exhaust cavity 23 and the exhaust duct 6.

[0088] Since the heat-generating components and compressor 3 are both located on the air intake path of cooling fan 7, the airflow is drawn in an orderly manner by the negative pressure of cooling fan 7 throughout the process. Compared with the traditional blowing scheme where the airflow diverges and impacts the surface of the components, resulting in turbulence and backflow, the airflow organization of this application is more orderly, avoiding the stagnation of hot air in the chamber, so that each stream of cooling air can give full play to the cooling effect, and cooling multiple heat-generating components one after another with the same airflow, thus achieving the balance of thermal management of the whole machine.

[0089] Specifically, in one embodiment, such as Figure 2As shown, the heating component includes an adsorption tower assembly 13, a control plate 15, and a main control valve 14. The adsorption tower assembly 13 and the inner shell 2 are arranged side by side, and the upper edge of the adsorption tower assembly 13 is higher than the inner shell 2 to form an installation space 16 above the inner shell 2. The control plate 15 and the main control valve 14 are disposed in the installation space 16.

[0090] This spatial layout design makes full use of the three-dimensional space resources within the air intake space 12. Without increasing the horizontal projected area of ​​the entire unit, the control board 15 and the main control valve 14 are integrated into the installation space 16 formed by the height difference between the adsorption tower assembly 13 and the inner shell 2, making the overall structure more compact and smaller in size. Moreover, the installation space 16 is located precisely on the main cooling airflow path between the air inlet 11 and the airflow inlet 51. The heat generated by the control board 15 and the main control valve 14 during operation can be carried away by the passing cooling airflow without the need for additional branch air ducts or independent fans, thus achieving auxiliary heat dissipation for the control board 15 and the main control valve 14.

[0091] In addition, the arrangement of the adsorption tower assembly 13 above the inner shell 2 allows the adsorption tower assembly 13 to be fully exposed to the cooling airflow of the air inlet space 12, resulting in a larger contact area between the airflow and the adsorption tower assembly 13 and more efficient heat exchange.

[0092] In a preferred embodiment of this application, such as Figure 2 , Figure 3 , Figure 8 As shown, the oxygen concentrator also includes a base assembly 4 located below the inner shell 2. The air inlet duct 5 and the air outlet duct 6 are both located inside the base assembly 4. The inner shell 2 and the base assembly 4 cooperate to form a receiving cavity 21. The base assembly 4 is provided with an air outlet 411 that communicates with the air outlet duct 6. The outer shell 1 or the base assembly 4 is provided with an air inlet 11 that communicates with the air inlet duct 5.

[0093] This application integrates the air inlet duct 5 and exhaust duct 6 of the heat dissipation air duct into the base assembly 4, eliminating the need for any complex air duct structure within the housing cavity 21 of the outer casing 1. This significantly frees up space within the housing cavity 21, facilitating the compact arrangement and maintenance of the compressor 3. Furthermore, since both the air inlet duct 5 and exhaust duct 6 are integrated into the base assembly 4, the paths for external airflow into and out of the housing cavity 21 are entirely within the base assembly 4. The housing cavity 21 serves merely as a passageway for airflow, rather than a duct carrier, thus avoiding the design difficulties, messy piping, and space occupation problems caused by dispersing the air inlet duct 5 and exhaust duct 6 in different locations within the oxygen concentrator.

[0094] In a preferred embodiment, such as Figure 1 , Figure 9As shown, the air inlet 11 is located on the outer casing 1, and the air outlet 411 is located on the base assembly 4, so that the overall cooling air of the oxygen generator enters from the side and exits from the bottom, preventing the exhaust hot air from being drawn back into the air inlet 11. Of course, the air inlet 11 can also be located on the base assembly 4, making the air inlet and exhaust positions more concentrated.

[0095] Furthermore, the base assembly 4, which integrates complete air intake and exhaust ducts 6, constitutes an independent modular unit. It can be prefabricated and tested separately on the production line (e.g., for airtightness and flow resistance testing), and then flexibly assembled under the oxygen concentrator casing 1 of different sizes or power ratings according to the requirements of the overall model. Even if different models have different internal oxygen-generating component layouts, there is no need to redesign the entire heat dissipation system; only the base assembly 4 needs to be matched, greatly improving the versatility of parts.

[0096] Specifically, such as Figure 2 , Figure 3 , Figure 8 As shown, the bottom of the inner shell 2 is an open structure, which cooperates with the base assembly 4 to form a receiving cavity 21.

[0097] Preferably, such as Figures 8 to 12 As shown, the base assembly 4 includes a bottom shell 41 and at least one partition. The bottom shell 41 and the partition form an air duct cavity with at least two layers of air duct space in the vertical direction. The air inlet duct 5 and the air outlet duct 6 are both located in the air duct cavity. The air inlet duct 5 and the air outlet duct 6 are isolated from each other, and at least one of them is formed by air duct spaces located in different layers.

[0098] By utilizing the multi-layered vertical space within the base assembly 4, the total path length of the heat dissipation airflow is significantly extended without increasing the projected area of ​​the base or the overall footprint of the oxygen concentrator. This longer airflow path not only provides more time for heat exchange, improving the cooling efficiency of core components such as the compressor 3, but more importantly, the extended path effectively reduces airflow velocity and turbulence intensity, thus significantly suppressing airflow noise and solving the problem of significant airflow noise caused by short airflow paths in existing technologies. Simultaneously, the upper and lower layered structure constructed through partitions spatially isolates the intake and exhaust airflow paths, avoiding the problem of reduced heat dissipation efficiency caused by mutual interference and short circuits in single-layer layouts.

[0099] This application does not limit the specific structure of the air intake duct 5 and the exhaust duct 6. In one embodiment, the air intake duct 5 is located in the air intake path of the cooling fan 7, and the exhaust duct 6 is located in the air outlet path of the cooling fan 7. After the airflow is pressurized and accelerated by the cooling fan 7, the flow rate is faster, and therefore noise is more likely to be generated in the exhaust path. Therefore, the exhaust duct 6 has a multi-layer structure to lengthen the path of the exhaust duct 6 in a limited space, which helps to slow down the airflow and reduce noise. Of course, the air intake duct 5 can also be set as a multi-layer structure. Alternatively, preferably, both the air intake duct 5 and the exhaust duct 6 are multi-layer structures.

[0100] It is understandable that when there is only one partition, a duct space is formed between it and the bottom wall of the bottom shell 41. Above the partition is the receiving cavity 21, which also constitutes a duct space. At this time, the duct cavity has two layers, upper and lower. When there are two partitions arranged at intervals, a duct space is formed between the lower partition and the bottom wall of the bottom shell 41, and a duct space is formed between the two partitions. At this time, the duct cavity can be regarded as three layers including the receiving cavity 21. And so on, the structure and number of layers of the duct cavity when there are more partitions.

[0101] like Figures 8 to 12 As shown, in a preferred embodiment, the partition includes a first partition 42 and a second partition 43 located above the first partition 42. The first partition 42 cooperates with the bottom wall of the bottom shell 41 to form a lower air duct space, and an upper air duct space is formed between the first partition 42 and the second partition 43. The air inlet duct 5 is connected to the air inlet cavity 22 through a first air outlet 421 provided on the first partition 42 and an air outlet 52 provided on the second partition 43. The exhaust duct 6 connects the exhaust cavity 23 and the exhaust outlet 411 through a second air outlet 422 provided on the first partition 42 and a third air outlet 431 provided on the second partition 43.

[0102] For air intake duct 5, such as Figures 9 to 12 As shown, the air intake duct 5 includes a first air intake section 53 located in the lower air intake space and a second air intake section 54 located in the upper air intake space. The first air intake section 53 is located upstream of the air intake duct 5 and is connected to the air intake port 11 through the airflow inlet 51 to allow external airflow to enter. The second air intake section 54 is located downstream of the air intake duct 5 and is connected to the air intake cavity 22 through the airflow outlet 52 to allow cooling air to enter the air intake cavity 22.

[0103] Furthermore, such as Figure 9 , Figure 11 , Figure 12As shown, the second air inlet section 54 includes a first diversion section 541 and a second diversion section 542 that are separated from each other and connected to the first air inlet section 53 respectively. The air outlets 52 are in two sets and are respectively set to correspond to the first diversion section 541 and the second diversion section 542. The horizontal projections of the two sets of air outlets 52 are located at different positions of the compressor 3.

[0104] like Figure 11 , Figure 12 As shown, a baffle is provided between the first baffle 42 and the second baffle 43 to ensure that the two streams travel independently in their respective channels until they reach the airflow outlet 52, thus avoiding internal crossflow and disturbance. In addition, the stream splitting design can also further reduce noise.

[0105] After the cooling air enters the first air inlet section 53 in the lower layer, it is guided upward and split into two independent airflows, which enter the two branch sections of the second air inlet section 54 in the upper layer, respectively. This achieves the initial distribution of the cooling air, and further guides the split cooling air to different locations of the compressor 3 within the air inlet cavity 22. This ensures that the cooling air flowing out from the two air outlets 52 does not blow onto the same area of ​​the compressor 3. The two cooling airflows can be directed to two different heat-generating parts of the compressor 3, achieving precise and directional parallel cooling. This three-dimensional, surrounding air supply method avoids the problem of localized overcooling and other areas remaining overheated that may be caused by single-point concentrated air supply, significantly improving the uniformity and effectiveness of heat dissipation for the compressor 3, thereby ensuring the stability and reliability of the oxygen concentrator during long-term operation. Through the layered and branched layout, the limited space can be utilized more effectively to organize the airflow, improving the targeting and overall efficiency of cooling.

[0106] Preferably, such as Figure 8 , Figure 9 As shown, the area of ​​the first partition 42 is larger than that of the second partition 43, so that it has an overlapping area corresponding to the second partition 43 vertically, and an open area that is offset vertically from the second partition 43. The airflow inlet 51 is opened in the offset area. This allows the airflow in the air intake space 12 to smoothly and quickly enter the air intake duct 5 by passing through only one partition, reducing the obstruction to the airflow and improving the air intake efficiency.

[0107] For exhaust duct 6, such as Figures 9 to 12As shown, the exhaust duct 6 includes a first exhaust section 61 located in the upper duct space and a second exhaust section 62 located in the lower duct space. The first exhaust section 61 is located upstream of the exhaust duct 6 and is directly connected to the exhaust cavity 23. The second exhaust section 62 is located downstream of the exhaust duct 6 and is connected to the exhaust port 411. Similarly, baffles are provided between the first partition 42 and the second partition 43, and between the first partition 42 and the bottom shell 41, to separate the air inlet ducts 5 and the exhaust ducts 6 located on each floor, so that the air inlet and exhaust air paths do not interfere with each other.

[0108] In summary, the overall heat dissipation airflow of the oxygen concentrator of this application is as follows: the outer shell 1 is provided with an air inlet 11, and the bottom shell 41 is provided with an exhaust outlet 411. External cooling air enters the air intake space 12 between the outer shell 1 and the inner shell 2 through the air inlet 11, cooling the adsorption tower assembly 13, the main control valve 14, and the control board 15 within this space. Then, it enters the air intake duct 5 inside the base assembly 4 through the air inlet 51 into the lower first air intake section 53. As it flows from the first air intake section 53 to the upper second air intake section 54, it is divided into two streams by the first air outlets 421 opened at different positions on the first partition 42. One stream enters the first diversion section 541, and the other enters the second diversion section 542. Then, they are blown into the air intake chamber 22 through their respective corresponding air outlets 52, and blown to different positions of the compressor 3. After the cooling air sweeps across the surface of the compressor 3 from one end to the other, it is drawn in by the cooling fan 7 and flows out from the air outlet 72 into the exhaust chamber 23. Then the cooling air flows downward into the first exhaust section 61 of the upper layer of the exhaust duct 6, and continues to flow downward into the second exhaust section 62 of the lower layer, and is finally discharged through the exhaust port 411.

[0109] Preferably, such as Figure 9 , Figure 11 , Figure 12 As shown, the first air inlet 421 and the air outlet 52 are staggered vertically, and / or the second air inlet 422 and the third air inlet 431 are staggered vertically.

[0110] For the air intake duct 5, the cooling air must flow upward from the first air outlet 421 of the first partition 42, and then pass through the staggered air outlets 52 of the second partition 43 before entering the air intake cavity 22. This staggered design forces the airflow to change direction during interlayer flow, preventing it from flowing directly upward. The airflow passes upward through the first air outlet 421, then flows laterally within the upper air duct space, and finally enters the air intake cavity 22 through the air outlet 52, forming a meandering path. This acts as a labyrinthine silencer, effectively blocking and attenuating the mechanical noise generated by components such as the compressor 3 and transmitted downward through the air outlet 52, as well as the high-speed airflow noise itself. Furthermore, the first partition 42 and the second partition 43 act as dust baffles, preventing dust and impurities in the air intake cavity 22 from falling directly into the depths of the air intake duct and clogging it.

[0111] For the exhaust duct 6, the vertical misalignment of the second air vent 422 and the third air vent 431 also serves to reduce noise and block dust. Through the above design, both noise reduction and dust prevention are achieved simultaneously without adding any extra parts.

[0112] Specifically, the staggered design scheme of the first air outlet 421 and the air outlet 52 of the air inlet duct 5, and the staggered design scheme of the second air outlet 422 and the third air outlet 431 of the exhaust duct 6 can be implemented together or one of them can be implemented separately, without any limitation.

[0113] This embodiment does not limit the location of the first partition 42. For example, it can be located above the bottom shell 41, covering the bottom shell 41 to form a lower air duct space. Alternatively, the first partition 42 can be located inside the bottom shell 41 to divide the internal space of the bottom shell 41 into upper and lower layers, with the lower layer forming the lower air duct space and the upper layer forming another air duct space.

[0114] Preferably, such as Figure 10 As shown, the bottom shell 41 is provided with a first mating cavity 412 and a second mating cavity 413. The first mating cavity 412 is used to cooperate with the partition to form at least a part of the air inlet duct 5, and the second mating cavity 413 is used to cooperate with the partition to form at least a part of the exhaust duct 6. The side wall of the bottom shell 41 is provided with an exhaust port 411 communicating with the second mating cavity 413. Since the cooling air in the exhaust duct 6 enters the second mating cavity 413 from top to bottom, and the exhaust port 411 is opened on the side wall of the bottom shell 41, the cooling air needs to make a turn of about 90° when it is discharged, thereby further reducing the kinetic energy of the airflow and improving the noise reduction effect.

[0115] Furthermore, such as Figure 10 As shown, the first mating cavity 412 surrounds at least a portion of the outer periphery of the second mating cavity 413.

[0116] The intake duct 5 surrounds the exhaust duct 6 from the outside, effectively forming a cold air insulation layer. This effectively reduces the heat radiation of the hot air in the exhaust duct 6 to the surrounding environment through the bottom shell 41, and also reduces the reverse heat transfer to the intake duct 5, ensuring stable intake air temperature. Furthermore, this surrounding layout maximizes the cross-sectional area and length of the intake duct 5 within a limited space, helping to reduce intake resistance, increase intake volume, and provide layout space for multi-branch intakes, achieving a highly compact design.

[0117] As a preferred embodiment of this application, such as Figures 13 to 15 As shown, the base assembly 4 is provided with a limiting structure for limiting the foot 33 of the compressor 3.

[0118] When compressor 3 vibrates or shakes, the amplitude of the shaking varies in different parts. Specifically, the shaking amplitude at cylinder liner 32 is usually greater than that at base 33. This makes limiting compressor 3 more difficult. If the limiting effect is poor, compressor 3 may violently impact the oxygen concentrator housing, causing structural damage or compressor 3 to detach.

[0119] This application addresses the characteristic of the small sway amplitude of the foot 33 during the operation of the compressor 3 by specifically limiting the foot 33. The limiting structure provides the foot 33 with necessary small range of freedom of movement, so that the vibration generated by the compressor 3 during operation can be reduced within the limiting space 451 and will not be directly transmitted to the whole machine casing. This significantly reduces the noise of the oxygen generator during operation and prevents resonance or fatigue damage to other structural components caused by vibration transmission.

[0120] Specifically, such as Figures 13 to 15 As shown, the base assembly 4 has a support platform 46 at its top, and the limiting structure includes a limiting member 45, which is fixed to the support platform 46, as shown. Figure 14 As shown, the limiting member 45 has a limiting sidewall 452 and a limiting top wall 453, wherein the limiting sidewall 452 surrounds the bottom foot 33 on three sides. The limiting sidewall 452 and the limiting top wall 453 cooperate with the supporting platform 46 to form a limiting space 451 for accommodating the bottom foot 33. The limiting space 451 is configured to allow the bottom foot 33 to move within the limiting space 451 and to prevent the bottom foot 33 from dislodging from the limiting space 451. The bottom of the limiting space 451 is open.

[0121] The presence of the limiting space 451 effectively restricts the maximum displacement of the foot 33. During the transportation and operation of the oxygen concentrator, it can reliably prevent the foot 33 of the compressor 3 from coming out of the limiting space 451, thereby preventing the cylinder 31 of the compressor 3 from violently impacting the sound insulation cavity or the oxygen concentrator housing, and avoiding problems such as damage to structural components or displacement and detachment of the compressor 3.

[0122] Furthermore, the limiting component 45 only partially encloses and limits the base 33, while most of the surfaces of the compressor 3, such as the cylinder block 31 and cylinder liner 32, are exposed to the air, which facilitates the timely dissipation of working heat and improves the heat dissipation effect of the compressor 3. At the same time, the structure in which the support component and the limiting component 45 are separately set and cooperate to form the limiting space 451 allows the compressor 3 to be installed first and then the limiting component 45, or the limiting component 45 to be installed first and then the compressor 3 to be placed, which provides flexibility for the assembly sequence of the production line and also facilitates the replacement of the compressor 3 without disassembling the entire support platform 46 during after-sales maintenance.

[0123] Specifically, the limiting member 45 can slide horizontally from a position away from the compressor 3 to a position closer to the compressor 3 to the installation position. The installation sequence is as follows: first, the compressor 3 is placed on the support platform 46, so that each foot 33 is positioned in its designated installation position on the support platform 46. Then, the limiting member 45 is slid horizontally from the outside to the inside to reach the installation position, so that the limiting member 45 and the support platform 46 enclose the feet 33, i.e., the feet 33 are located within the limiting space 451. During disassembly, the limiting member 45 is slid in the opposite direction to open the installation position, at which point the feet 33 are exposed on the installation platform.

[0124] For any parts not mentioned in this application, existing technologies may be used or referenced.

[0125] The various embodiments in this specification are described in a progressive manner. The same or similar parts between the various embodiments can be referred to each other. Each embodiment focuses on describing the differences from other embodiments.

[0126] The above description is merely an embodiment of this application and is not intended to limit the scope of this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the scope of the claims of this application.

Claims

1. An oxygen concentrator, comprising a shell and an inner shell disposed inside the shell, wherein the inner shell forms a receiving cavity, characterized in that, The accommodating cavity includes a mutually separated air inlet cavity and an air outlet cavity. The air inlet cavity is equipped with a compressor and a cooling fan. The cooling fan has an air intake and an air outlet. The oxygen generator also includes an air inlet duct and an air outlet duct. The air inlet duct has an air outlet communicating with the air inlet cavity. The air intake and the air outlet are located on opposite sides of the compressor and are both oriented towards the compressor. The air outlet communicates with the air outlet duct through the air outlet cavity.

2. The oxygen generator according to claim 1, characterized in that, The compressor is a piston compressor, which includes a cylinder and a cylinder liner protruding from the surface of the cylinder. The cooling fan is arranged corresponding to the cylinder liner, and the air intake is arranged facing the cylinder liner.

3. The oxygen generator according to claim 2, characterized in that, The cylinder liner protrudes upward from the top of the cylinder body, the cooling fan is located above the cylinder liner, the air intake is located at the bottom of the cooling fan and faces the cylinder liner, and the air outlet is located on the bottom wall of the air intake chamber and faces upward.

4. The oxygen generator according to claim 3, characterized in that, The bottom wall of the air inlet cavity is provided with a mating groove that matches the bottom shape of the cylinder body. At least a portion of the cylinder body is accommodated in the mating groove, and the airflow outlet is located in the mating groove.

5. The oxygen generator according to claim 1 or 2, characterized in that, The oxygen generator also includes an air guide, which covers the outer periphery of a portion of the compressor to form an air intake channel that connects to the air inlet. There is an air intake gap between the air guide and the outer wall of the compressor.

6. The oxygen generator according to claim 5, characterized in that, The suction channel has an inlet side sleeved on the outside of the compressor and an outlet side connected to the suction port. The suction channel is provided with guide vanes arranged in a spiral shape from the inlet side to the outlet side to form a spiral air duct in the suction channel.

7. The oxygen generator according to claim 1, characterized in that, The outer shell is provided with an air inlet, and an air intake space is formed between the outer shell and the inner shell. The inner shell is a closed structure, and the air intake cavity is connected to the air intake space through the air intake duct.

8. The oxygen generator according to claim 1, characterized in that, The outer shell is provided with an air inlet, and an air intake space is formed between the outer shell and the inner shell. The air intake duct has an airflow inlet, which is disposed opposite to the air inlet on both sides of the inner shell. At least one heating element is disposed between the air inlet and the airflow inlet.

9. The oxygen generator according to claim 8, characterized in that, The heating element includes an adsorption tower assembly, a control board, and a main control valve. The adsorption tower assembly and the inner shell are arranged side by side, and the upper edge of the adsorption tower assembly is higher than the inner shell to form an installation space above the inner shell. The control board and the main control valve are disposed in the installation space.

10. The oxygen generator according to claim 1, characterized in that, The oxygen generator also includes a partition disposed within the accommodating cavity, and the exhaust cavity is located inside the partition; or the partition and the inner shell cooperate to form the exhaust cavity.

11. The oxygen generator according to claim 1, characterized in that, The oxygen generator also includes a base assembly located below the inner shell. The air inlet duct and the air outlet duct are both disposed inside the base assembly. The inner shell and the base assembly cooperate to form the receiving cavity. The base assembly is provided with an air outlet communicating with the air outlet duct. The outer shell or the base assembly is provided with an air inlet communicating with the air inlet duct.

12. The oxygen generator according to claim 11, characterized in that, The base assembly includes a bottom shell and at least one partition. The bottom shell and the partition form an air duct cavity having at least two layers of air duct space in the vertical direction. The air inlet duct and the air outlet duct are both located within the air duct cavity. The air inlet duct and the air outlet duct are isolated from each other, and at least one of them is formed by the air duct space located in different layers being connected.

13. The oxygen generator according to claim 12, characterized in that, The partition includes a first partition and a second partition located above the first partition. The first partition cooperates with the bottom wall of the bottom shell to form a lower air duct space, and an upper air duct space is formed between the first partition and the second partition. The air inlet duct is connected to the air inlet cavity through a first air outlet provided on the first partition and an air outlet provided on the second partition. The air outlet duct connects the air outlet cavity to the air outlet through a second air outlet provided on the first partition and a third air outlet provided on the second partition.

14. The oxygen generator according to claim 13, characterized in that, The first air inlet and the air outlet are vertically offset, and / or the second air inlet and the third air inlet are vertically offset.

15. The oxygen generator according to claim 13, characterized in that, The air inlet duct includes a first air inlet section located in the lower air duct space and a second air inlet section located in the upper air duct space. The second air inlet section includes a first diversion section and a second diversion section that are separated from each other and respectively connected to the first air inlet section. The air outlets are in two sets and are respectively arranged corresponding to the first diversion section and the second diversion section. The horizontal projections of the two sets of air outlets are respectively located at different positions of the compressor.

16. The oxygen generator according to claim 11, characterized in that, The base assembly is provided with a limiting structure for limiting the foot position of the compressor.

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