A portable air pump

Abstract

This invention relates to a portable air pump, belonging to the technical field of air pumps. The design parameter H ranges from 60mm to 88mm; the design parameter W ranges from 23mm to 35mm; and the design parameter L ranges from 39mm to 49mm. The portable air pump can inflate an object to a pressure P, where the pressure P ranges from 105psi to 150psi. The cylinder of the portable air pump has a pre-compression volume of V1 and a post-compression volume of V2, satisfying 16 ≤ V1 / V2 ≤ 60. This invention ensures that the air pump is sufficiently compact for easy carrying and storage without affecting its inflation function. By rationally controlling the compression ratio, the motor can operate efficiently under lower loads, improving inflation efficiency and extending the motor's lifespan.

Description

Technical Field

[0001] This invention belongs to the field of air pump technology, and relates to the technology of optimizing the airflow path of an air pump, specifically to a portable air pump. Background Technology

[0002] Portable air pumps are widely used tools for inflating sports equipment, especially in emergency or outdoor environments. Their small size and portability make them a common inflation device. With rising living standards and increasing personalized needs, the market demand for portable air pumps is gradually growing, and users are placing higher demands on their performance, efficiency, and convenience.

[0003] However, existing portable air pumps often present a trade-off between performance and portability. Due to the need to provide high-pressure inflation, air pumps are typically designed to be large, making it difficult to achieve a sufficiently compact size and weight, thus impacting portability. Simultaneously, the cylinder's compression ratio directly affects inflation efficiency and motor load. If the cylinder's compression ratio is designed too high, the workload required for gas compression increases, placing an excessive burden on the motor and potentially leading to overheating or overload, affecting the device's durability and stability. Conversely, if the compression ratio is too low, high-pressure inflation cannot be achieved, resulting in decreased inflation efficiency and potentially failing to meet the high-pressure requirements of practical use. Therefore, ensuring both inflation pressure and efficiency while maintaining good portability, stability, and high performance remains a significant challenge in current technology design. Summary of the Invention

[0004] To address the aforementioned problems in the prior art, the present invention provides a portable air pump.

[0005] To achieve the above objectives, the technical solution adopted by the present invention is as follows:

[0006] Provide a portable air pump, having at least the following features:

[0007] The design parameter H represents the numerical value of the air pump housing height;

[0008] The design parameter W represents the width of the air pump housing.

[0009] The design parameter L represents the numerical value of the length of the air pump housing;

[0010] The design parameter H is in the range of 60mm to 88mm.

[0011] The design parameter W has a range of 23mm to 35mm.

[0012] The design parameter L has a range of 39mm to 49mm.

[0013] Furthermore, the aforementioned design parameters H, W, and L can take any value within their respective ranges, which has the following properties:

[0014] The portable air pump can inflate the object to be inflated to pressure P;

[0015] Furthermore, the pressure P ranges from 105 psi to 150 psi;

[0016] The volume of the portable air pump's cylinder before compression is V1:

[0017]

[0018] The compressed volume is V2:

[0019]

[0020] And it satisfies:

[0021] 16≤V1 / V2≤60;

[0022] Where D4 is the inner diameter of the cylinder, K is the stroke of the cylinder, s is the clearance of the cylinder, t is the thickness of the air outlet, and d is the diameter of the air outlet.

[0023] The stroke of the cylinder is K, and it satisfies:

[0024] K = 2 * Q, where Q is the eccentricity of the eccentric wheel of the portable air pump.

[0025] Preferably, the stroke K of the cylinder is in the range of 8mm to 12mm.

[0026] Preferably, the clearance s of the cylinder is in the range of 0.2mm to 0.5mm;

[0027] Furthermore, the clearance s refers to the width between the end face of the piston disc and the inner wall of the cylinder when the piston disc reaches the maximum compression position.

[0028] Preferably, the diameter d of the air outlet of the cylinder is in the range of 3mm to 4mm;

[0029] And / or, the thickness t of the air outlet of the cylinder is in the range of 0.5 mm to 3 mm.

[0030] Preferably, it includes:

[0031] case;

[0032] The power module is located inside the housing;

[0033] The drive module is located inside the housing and is electrically connected to the power module.

[0034] Cylinder and air pump chamber;

[0035] The cylinder and the air-inflating chamber are connected in one direction only.

[0036] Preferably, it includes a connecting rod, and a piston disc is provided at the end of the connecting rod;

[0037] An annular groove is formed along the circumferential wall of the piston disc;

[0038] Furthermore, a piston ring is embedded in the annular groove;

[0039] Wherein, along the connecting rod axis, the axial dimension of the annular groove is H1, and the axial dimension of the piston ring is X;

[0040] M1-X = C1, where C1 ranges from 0.2 mm to 2 mm;

[0041] An airflow channel is provided at the bottom of the annular groove;

[0042] Furthermore, the piston disc is provided with a through airflow port, which corresponds to the position of the airflow groove.

[0043] Preferably, the piston disc includes a first sealing disc and a second sealing disc;

[0044] The annular groove is located between the first sealing disc and the second sealing disc;

[0045] Wherein, along the connecting rod radial direction, the maximum diameter of the first sealing disc is D1, the maximum diameter of the second sealing disc is D2, the maximum diameter of the outer ring surface of the piston ring is L2, and the inner diameter of the cylinder is D4;

[0046] Where L2≥D4; D4>D2>D1.

[0047] Preferably, L2-D4 = C2, and the value of C2 ranges from 0mm to 1mm;

[0048] Furthermore, 0mm≤D4-D2≤0.85*X;

[0049] Furthermore, D1≥L2-X.

[0050] Preferably, an airflow space is formed between the second wall surface and the eccentric wheel, and the air intake port of the cylinder is connected to the airflow space.

[0051] Preferably, the air-inflating chamber has an air-inflating port.

[0052] Preferably, the air-inflating chamber is provided with a detection port;

[0053] The detection port is connected to a detection cavity, and a pressure detection device is installed in the detection cavity.

[0054] Preferably, the cylinder and the air chamber are connected by a one-way flow guidance structure, the one-way flow guidance structure comprising:

[0055] A valve plate is disposed in the air pumping chamber and covers the communication port between the cylinder and the air pumping chamber;

[0056] A sealing element is disposed at the communication port and in contact with the valve plate.

[0057] Preferably, it includes a display module, which is disposed in the housing.

[0058] This invention provides a portable air pump, and the beneficial effects of this invention are as follows:

[0059] The portable air pump of this invention significantly improves device performance and user experience by rationally setting the value range of design parameters H, W, and L and optimizing the cylinder compression ratio. This ensures the air pump is compact enough for easy carrying and storage without compromising its inflation function. This makes the air pump more flexible in practical use, allowing users to easily place it in small spaces such as vehicles or backpacks for convenient use anytime.

[0060] The cylinder compression ratio V1 / V2 is set between 16 and 60 to avoid the negative effects of excessively high or low compression ratios. A suitable compression ratio ensures efficient gas compression during inflation while effectively reducing the motor load. An excessively high compression ratio will overload the motor, affecting its lifespan and stability, while an excessively low compression ratio will result in poor inflation performance, failing to achieve the expected high-pressure output. By rationally controlling the compression ratio, this invention enables the motor to operate efficiently under lower loads, improving inflation efficiency and extending the motor's lifespan. Attached Figure Description

[0061] Figure 1 This is a perspective view of the portable air pump proposed in this invention;

[0062] Figure 2 This is a side view of the portable air pump proposed in this invention;

[0063] Figure 3 This is a rear view of the portable air pump proposed in this invention;

[0064] Figure 4 This is a top view of the portable air pump proposed in this invention;

[0065] Figure 5 This is a front view of the portable air pump proposed in this invention;

[0066] Figure 6 This is one of the structural diagrams of the concealed housing of the portable air pump proposed in this invention;

[0067] Figure 7 This is the second structural diagram of the concealed housing of the portable air pump proposed in this invention;

[0068] Figure 8 This is a cross-sectional view of the portable air pump proposed in this invention;

[0069] Figure 9 This is a perspective view of the cylinder in the portable air pump proposed in this invention;

[0070] Figure 10 for Figure 9 A cross-sectional view of the structure shown;

[0071] Figure 11 This is a front view of the connecting rod in the portable air pump proposed in this invention;

[0072] Figure 12 for Figure 11 A cross-sectional view of the structure shown;

[0073] Figure 13 This is a perspective view of the connecting rod in the portable air pump proposed in this invention.

[0074] Explanation of reference numerals in the attached figures:

[0075] 1. Housing; 101. First wall surface; 102. Second wall surface; 2. Power module; 3. Drive module; 401. Cylinder; 4011. Air inlet port; 402. Air pumping chamber; 4021. Air pumping port; 5. Piston ring; 6. Transmission component; 601. Eccentric wheel; 602. Connecting rod; 6021. Piston disc; 6022. Annular groove; 7. Airflow space; 8. Detection chamber; 801. Air pressure detection device; 9. One-way flow guide structure; 901. Valve plate; 902. Seal; 10. Display module; 11. Airflow groove; 12. Airflow port; 1301. First sealing disc; 1302. Second sealing disc. Detailed Implementation

[0076] 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. 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.

[0077] Please see Figure 1 - Figure 13 As shown, the specific embodiments provided by the present invention are as follows:

[0078] like Figures 1 to 9 As shown, the first embodiment of the present invention proposes a portable air pump, the purpose of which is to provide a structural layout for a portable air pump, including:

[0079] Casing 1;

[0080] The power module 2 is disposed inside the housing 1 and located on one side of the first wall 101;

[0081] The drive module 3 is disposed inside the housing 1 and adjacent to the bottom surface of the housing 1;

[0082] Wherein, the height direction of the power module 2 is consistent with the height direction of the housing 1, and the axial direction of the drive module 3 is consistent with the length direction of the housing 1;

[0083] An airflow cavity is disposed inside the housing 1 and located on one side of the second wall 102;

[0084] The first wall surface 101 and the second wall surface 102 are two opposing side walls of the housing 1;

[0085] The axis of the airflow cavity is aligned with the height direction of the housing 1;

[0086] Furthermore, the airflow cavity includes a cylinder 401 and an air-inflating cavity 402;

[0087] The cylinder 401 and the air pumping chamber 402 are connected in one direction only;

[0088] Furthermore, a piston ring 5 is slidably connected inside the cylinder 401;

[0089] The piston ring 5 is connected to the drive module 3 via a transmission component 6 to form piston movement within the cylinder 401;

[0090] The air chamber 402 has a height M1, and the cylinder 401 has a height M2;

[0091] Where M1+M2>1 / 2H, and M2≥M1;

[0092] H is the height of the shell 1.

[0093] In this embodiment, the housing 1 serves as the external frame of the entire air pump, providing necessary structural support and securing internal components. Furthermore, the housing 1 does not have a clearly defined air intake structure, i.e., an air inlet. External air enters the housing 1 through the mounting gap. Compared to traditional portable air pump designs, existing technologies typically require a specially designed air inlet or air valve to guide external air in. However, this embodiment reduces the need for a prominent air inlet design, simplifying the overall structure and the number of internal components. By utilizing the mounting gap of the housing 1 as an air intake channel, manufacturing costs are reduced, potential failure points are decreased, and equipment reliability is improved. Although there is no explicit air inlet, this embodiment ensures the stability and controllability of airflow by controlling the mounting gap of the housing 1. It also prevents impurities and dust from entering the equipment, protecting internal components and extending the equipment's lifespan.

[0094] The power module 2 is installed on one side of the first wall 101 of the housing 1, and its height direction is consistent with the height direction of the housing 1. The power module 2 is a rechargeable battery, which is responsible for providing a stable power supply to the drive module 3.

[0095] The drive module 3 is located near the bottom of the housing 1, with its axis aligned with the length of the housing 1. The drive module 3 includes an electric motor, which converts electrical energy into mechanical energy via a transmission component 6 to drive the piston.

[0096] The airflow cavity is located on one side of the second wall 102 of the housing 1, with its axis aligned with the height direction of the housing 1. The airflow cavity includes a cylinder 401 and an air-inflating cavity 402, which are connected by a one-way communication structure to ensure that gas can only flow from the cylinder 401 to the air-inflating cavity 402, thus preventing gas backflow.

[0097] In existing technology, the cylinder 401 of a portable air pump is typically directly connected to the air inlet 4021, meaning the cylinder 401 is connected to the pressure inside the tire. As the internal tire pressure gradually increases, the pressure that the cylinder 401 needs to overcome increases, leading to a significant increase in the energy required for piston movement, resulting in the following problems:

[0098] When cylinder 401 is directly connected to air inlet 4021, as the air pressure rises, the pressure inside the tire is directly transmitted to the piston chamber. This means that the piston must overcome increasingly greater external pressure during each compression process, and as the pressure increases, the driving force required for the piston's movement also increases. To overcome these external pressures, drive module 3 needs to consume more energy. With this structure, the air pump is inefficient, especially when facing high-pressure inflation demands, often leading to overwork of drive module 3, thus affecting the equipment's lifespan and inflation efficiency.

[0099] Because cylinder 401 is directly affected by the internal pressure of the tire, the piston's movement requires greater force for compression. This results in reduced airflow during each compression, prolonged inflation time, and a significant decrease in inflation efficiency. Furthermore, the frequent piston movement and high energy consumption mean that the device cannot provide sufficient airflow and pressure for a certain period, impacting the user experience, especially in scenarios requiring high-pressure inflation.

[0100] During high-pressure inflation, the pressure in cylinder 401 directly interacts with the internal tire pressure, increasing the workload of drive module 3, especially in the later stages of inflation. To overcome the high pressure, drive module 3 needs to provide greater power output, which may lead to overload risks and even shorten the service life of drive module 3.

[0101] Based on this, by setting an additional air-pressing chamber 402 between the cylinder 401 and the air-pressing port 4021, and connecting the cylinder 401 and the air-pressing chamber 402 in one direction, the impact of high pressure on piston movement and energy consumption can be effectively mitigated.

[0102] Specifically, with the addition of the inflation chamber 402, the cylinder 401 and the inflation port 4021 are no longer directly connected. Instead, the airflow is buffered and regulated through the inflation chamber 402. The inflation chamber 402 essentially provides an additional air storage space, ensuring that the airflow has undergone pressure regulation before entering the inflation port 4021, thus preventing the cylinder 401 from directly experiencing drastic changes in tire internal pressure. This reduces the pressure the piston needs to overcome during movement, thereby lowering the power consumption of the drive module 3 and improving inflation efficiency.

[0103] Piston ring 5 is installed inside cylinder 401 and slidably connected to the inner wall of cylinder 401. Piston ring 5 is connected to drive module 3 through transmission component 6 to generate piston movement.

[0104] Based on the above, the optimized layout of the power module 2 and the drive module 3 allows the airflow cavity to occupy nearly half of the space inside the housing 1. This layout optimization not only increases the volume of the airflow cavity but also provides the cylinder 401 with a larger effective working space, thereby significantly improving the overall performance of the portable air pump.

[0105] Specifically, cylinder 401 has a longer working stroke and a larger volume, allowing it to accommodate more airflow and provide higher air pressure output with each piston movement. Compared to the low efficiency caused by space limitations and short piston stroke in traditional technologies, this structure makes full use of the space within the housing 1, effectively expanding the height of the airflow chamber.

[0106] By increasing the volume of cylinder 401 and optimizing the airflow path, the portable air pump can deliver higher air pressure and more stable airflow at the same power. Thanks to the larger piston stroke and higher gas storage capacity, the device can quickly accumulate enough gas to achieve higher output pressure, meeting more complex inflation needs. It performs well in both high-pressure inflation environments and applications requiring stable airflow output.

[0107] The optimized layout of the power module 2 and drive module 3 makes the entire portable air pump design more compact. The internal space of the housing 1 is effectively utilized, ensuring sufficient airflow chamber volume without adding extra size and weight. This structure allows the portable air pump to maintain a small size while achieving higher efficiency, meeting the dual needs of modern users for portability and efficiency.

[0108] Furthermore, it was discovered that, due to the power limitations of the power module 2 and drive module 3 in the portable air pump, a higher piston chamber height is not necessarily better. The reason is as follows:

[0109] As the height of cylinder 401 increases, the piston stroke becomes longer, meaning that more air needs to be compressed and drawn in with each piston movement. This results in drive module 3 requiring more power for each movement. If cylinder 401 is too tall, the required power exceeds the output capacity of power module 2. Even if the battery or power module 2 can provide sufficient power, the charging process may be inefficient due to insufficient power. This can lead to unstable equipment operation or even failure to reach the desired pressure.

[0110] While a taller cylinder 401 can increase the airflow per stroke, an excessively long piston stroke can lead to energy waste. Due to the limited power of power module 2 and drive module 3, if the height of cylinder 401 is too large, the piston may not be able to fully and effectively utilize the energy of each stroke. Prolonged strokes and higher gas flow rates result in energy loss, thus reducing the inflation efficiency of the device. An excessively long piston stroke limits the efficiency of each airflow and the increase in air pressure, thereby extending inflation time and increasing the device's power consumption.

[0111] Therefore, in order to find the optimal balance between ensuring the efficiency and power limitations of the portable air pump, this invention optimizes its performance by limiting the height of the cylinder 401 and the air chamber 402. Specifically, limiting the height of the cylinder 401 and the air chamber 402 is mainly aimed at ensuring that the device can efficiently complete the inflation task under power constraints, while avoiding excessive energy consumption or increased burden on the device.

[0112] In this embodiment of the invention, the heights of the cylinder 401 and the air pumping chamber 402 are defined as follows:

[0113] M1+M2>1 / 2H, where M1 is the height of the air chamber 402, M2 is the height of the cylinder 401, and H is the height of the housing 1.

[0114] At the same time, M2≥M1, that is, the height of cylinder 401 should be greater than or equal to the height of air chamber 402, to ensure that the piston compression is sufficient, but not to excessively increase the total volume of air chamber.

[0115] This ensures sufficient air compression during each piston movement while avoiding excessive power consumption and inefficient charging caused by an overly tall cylinder 401.

[0116] The second embodiment of the present invention provides a portable air pump, and based on the first embodiment, the transmission component 6 includes:

[0117] Eccentric wheel 601 and connecting rod 602;

[0118] The eccentric wheel 601 is connected to the drive end of the drive module 3;

[0119] One end of the connecting rod 602 is eccentrically connected to the eccentric wheel 601, and the other end is connected to the piston ring 5;

[0120] In the height direction of the housing 1, the air inlet port 4011 of the cylinder 401 is located above the eccentric wheel 601.

[0121] In this embodiment, the transmission component 6 includes an eccentric wheel 601 and a connecting rod 602. The eccentric wheel 601 is connected to the drive end of the drive module 3 (referring to the motor). The rotation of the eccentric wheel 601 causes the other end of the connecting rod 602 to drive the piston ring 5 to generate piston movement. The eccentric structure of the eccentric wheel 601 makes the piston movement regular and stable, effectively controlling the compression and intake processes of the piston, thereby improving the stability of the airflow and the pumping efficiency.

[0122] Based on the above, this embodiment further optimizes the position of the air inlet port 4011 of the cylinder 401. In the height direction of the housing 1, the air inlet port 4011 of the cylinder 401 is positioned above the eccentric wheel 601. Since the housing 1 in this embodiment does not have a significant air inlet, external air can only enter the interior through the gaps in the housing 1. When the eccentric wheel 601 rotates, the rotation of the eccentric wheel 601 generates airflow disturbance inside the housing 1, thereby causing the airflow to be disturbed at the gaps in the housing 1 and accelerated towards the cylinder 401.

[0123] The rotation of the eccentric wheel 601 creates airflow disturbance through its eccentric structure. This airflow disturbance can effectively avoid the phenomenon of stagnant airflow or inefficient air intake, allowing air to enter the cylinder 401 more smoothly.

[0124] The disturbance caused by the eccentric wheel 601 allows for better replenishment of external air, ensuring that the cylinder 401 can stably and adequately draw in air during the intake phase.

[0125] like Figures 9 to 13 As shown, the third embodiment of the present invention proposes a portable air pump, and based on the previous embodiment, a piston disc 6021 is provided at the end of the connecting rod 602;

[0126] An annular groove 6022 is formed along the circumferential wall of the piston disc 6021;

[0127] Furthermore, the piston ring 5 is movably fitted within the annular groove 6022 and is configured to have a sliding displacement along the height direction of the annular groove 6022.

[0128] In this embodiment, by providing an annular groove 6022 and embedding the piston ring 5 therein, good contact between the seal 902 and the piston disc 6021 can be ensured, avoiding gas leakage problems. The annular groove 6022 allows the seal 902 to maintain a stable sealing state during piston movement, ensuring effective compression and transmission of gas within the cylinder 401. The piston ring 5 is configured to slide along the height direction of the annular groove 6022, allowing the seal 902 to more flexibly adapt to changes within the cavity during piston movement. The sliding displacement reduces friction, improves the smoothness and efficiency of piston movement, and avoids wear or obstruction caused by fixing the seal 902.

[0129] Wherein, along the axis of the connecting rod 602, the axial dimension of the annular groove 6022 is H1, and the axial dimension of the piston ring 5 is X;

[0130] M1-X = C1, where C1 ranges from 0.2mm to 2mm;

[0131] An airflow groove 11 is disposed at the bottom of the annular groove 6022;

[0132] Furthermore, the piston disc 6021 is provided with a through airflow port 12, which corresponds to the position of the airflow groove 11.

[0133] In this embodiment, an annular groove 6022 is provided on the circumferential wall of the piston disc 6021, and a piston ring 5 is installed in the groove. The design of the annular groove 6022 gives the piston ring 5 a certain degree of freedom within the groove. Unlike the traditional fixed sealing ring or cup design, the piston ring 5 can make slight movements and adjustments during the reciprocating motion of the piston. This design means that the piston ring 5 no longer relies on close contact with the inner wall of the cylinder 401 to achieve air intake. Instead, air is guided into the cylinder 401 through the airflow groove 11 provided in the annular groove 6022 and the airflow port 12 on the piston disc 6021, thereby ensuring that sufficient air intake can be maintained in the miniaturized cylinder 401.

[0134] During the piston's return stroke, connecting rod 602 and piston disc 6021 displace in the return direction. Due to friction with the inner wall of cylinder 401, piston ring 5 displaces in the annular groove 6022 in the opposite direction to the return stroke. At this time, the airflow groove 11 is completely exposed and located in the outer region of cylinder 401, allowing air to smoothly enter cylinder 401 through the airflow groove 11 and airflow port 12 for rapid air replenishment. This design does not rely on deformation of piston ring 5 or gaps with the inner wall of cylinder 401, effectively avoiding insufficient air intake under miniaturization conditions. As the piston return stroke completes, piston ring 5 readjusts its position after the friction disappears, partially covering the airflow groove 11, ready for the next compression stroke.

[0135] Based on the above, it was further discovered that the intake volume is not necessarily better the larger it is. Excessive intake volume will increase airflow resistance, which in turn will cause many problems with the motor (as described in the background art). Therefore, it is further proposed that the axial dimension of the annular groove 6022 is H1 and the axial dimension of the piston ring 5 is X in the direction along the axis of the connecting rod 602.

[0136] H1-X = C1, where C1 ranges from 0.2mm to 2mm.

[0137] In this embodiment, it was found that:

[0138] When C1 is too large, the gap between the annular groove 6022 and the piston ring 5 becomes too large, which will lead to a poor sealing effect of the piston ring 5, making it easy for gas to leak from the gap and reducing the system's working efficiency.

[0139] An excessively high C1 will cause uneven airflow velocity and pressure distribution, resulting in fluctuations in intake volume, leading to unstable motor operation and affecting overall performance. Due to gas leakage, the system needs to consume more power to maintain airflow, thereby increasing the burden on the motor and energy consumption, and reducing equipment efficiency.

[0140] When C1 is too small, the gap between piston ring 5 and annular groove 6022 is too small, which will cause the airflow path to be too narrow, restrict the intake volume, increase the airflow resistance, and prevent the system from achieving the required intake volume.

[0141] Insufficient clearance leads to frequent mechanical contact between piston ring 5 and annular groove 6022, increasing friction and causing accelerated wear of parts, affecting piston sliding performance and lifespan. Due to insufficient intake and increased airflow resistance, the motor will face a higher load, potentially causing overheating or damage.

[0142] Based on this, by setting C1 within the range of 0.2mm to 2mm, especially the value of 1mm selected in this embodiment, the following beneficial effects can be achieved:

[0143] This difference in airflow balance ensures that excessive airflow will not increase airflow resistance, nor will insufficient airflow negatively impact system efficiency, thus achieving a balance and control of the airflow volume. The appropriate gap ensures moderate resistance to airflow as it passes through the annular groove 6022, maintaining a stable airflow volume while preventing excessive airflow turbulence and ensuring stable motor load. The suitable difference effectively reduces friction between the piston ring 5 and the annular groove 6022, reducing component wear and extending equipment lifespan. This design reduces energy consumption while ensuring precise airflow control and improving the overall system efficiency.

[0144] In general, setting the value of C1 to be between 0.2 mm and 2 mm can achieve a balance in terms of sealing performance, airflow resistance, and equipment durability, thereby improving the overall performance of the system.

[0145] Furthermore, the dimensional fit between the piston ring 5 and the annular groove 6022 optimizes the air intake path and precisely controls the air intake volume during the movement of the connecting rod 602. This not only improves the efficiency of the air pump but also facilitates the miniaturization of the device, meeting the needs of portable applications. Simultaneously, the appropriate piston ring 5 size enhances the sealing effect, reduces air leakage, and further lowers the motor's energy consumption.

[0146] In summary, by reasonably setting the axial dimension ratio of piston ring 5 and annular groove 6022, this embodiment successfully solves the problems of increased airflow resistance and excessive motor load caused by excessive air intake, thereby improving the overall performance and reliability of the miniaturized air pump.

[0147] The fourth embodiment of the present invention provides a portable air pump, and based on the previous embodiment, the piston disc 6021 includes a first sealing disc 1301 and a second sealing disc 1302;

[0148] The annular groove 6022 is located between the first sealing disc 1301 and the second sealing disc 1302;

[0149] Among them, in the direction along the diameter line of the connecting rod 602, the maximum diameter of the first sealing disc 1301 is D1, the maximum diameter of the second sealing disc 1302 is D2, and the maximum diameter of the outer ring surface of the piston ring 5 is L2; the inner cavity diameter of the cylinder 401 is D4;

[0150] Among them, L2≥D4; D4>D2>D1.

[0151] In this embodiment, it is ensured that the structure of the piston disc 6021 can provide a progressive sealing effect in a limited space (it should be noted that the sealing here does not mean complete sealing, but refers to controlling the air leakage volume and air intake volume on the basis of a certain air leakage volume and air intake volume). Specifically:

[0152] D1<D2: This relationship indicates that the diameter of the second sealing disc 1302 is slightly larger than that of the first sealing disc 1301. The purpose of this design is that when the connecting rod 602 moves in the cylinder 401, the design of the second sealing disc 1302 tends to control the sealing of the air intake volume and air leakage volume, rather than complete sealing. This design helps to achieve efficient air intake in a miniaturized air pump while maintaining reasonable air flow regulation. Specifically:

[0153] There is a certain gap between the second sealing disc 1302 and the inner wall of the cylinder 401, allowing air flow to enter the air flow groove 11 through this gap. This design aims to control the air entry path and ensure that the air intake volume is optimized. The existence of this gap enables air to enter the air flow groove 11 through the gap between the second sealing disc 1302 and the inner wall of the cylinder 401 during the piston return stroke, and enter the cylinder 401 through the air flow port 12, thereby achieving air replenishment. In this way, during the entire piston return stroke, the air flow path is controlled rather than completely blocked.

[0154] Of course, the gap size between the second sealing disc 1302 and the inner wall of the cylinder 401 can be precisely designed to ensure that during the air intake process, air can smoothly enter the air flow groove 11 in a controlled state. This gap regulates the air intake volume, enabling sufficient air volume to be inhaled each time the piston returns, ensuring that the air pump can achieve an efficient air intake effect.

[0155] This design avoids the problem of blocked air flow under the traditional complete sealing design. By controlling the gap, the air flow entry volume is optimized, thereby improving the working efficiency of the air pump under miniaturized conditions.

[0156] In this embodiment, the second sealing disc 1302 is not completely sealed, thus avoiding the air intake restriction problem caused by a complete seal. By allowing some airflow to enter through the gap between the second sealing disc 1302 and the inner wall of the cylinder 401, smooth airflow is ensured, effectively preventing air accumulation during compression. This controlled sealing design can precisely regulate leakage to a certain extent, ensuring that air can fully enter the cylinder 401 during intake, while providing sufficient sealing during compression to reduce unnecessary air leakage. This balanced design ensures sufficient air intake while controlling leakage, making the equipment operate more stably.

[0157] Because the gap design of the second sealing disc 1302 ensures unobstructed air intake, the motor does not need to frequently run to compensate for insufficient air intake during operation, thus significantly reducing motor idle time. Furthermore, this design avoids incomplete compression caused by air obstruction, ensuring efficient motor operation in each working cycle.

[0158] Furthermore, due to the relationship that L2≥D4, the outer ring surface of piston ring 5 can contact the inner wall of cylinder 401 more closely, thereby providing a better sealing effect during compression.

[0159] Furthermore, 0mm≤D4-D2≤0.85*X:

[0160] Specifically, the difference between the inner diameter D4 of cylinder 401 and the diameter D2 of the second sealing disc 1302 can be zero, meaning that under the tightest fit, the diameter of the second sealing disc 1302 is equal to the inner diameter of cylinder 401. This tight fit helps achieve excellent sealing performance, especially when the system is operating at high pressure, minimizing gas leakage.

[0161] The condition D4-D2≤0.85*X limits the difference to no more than 0.85 times the axial dimension X of piston ring 5. This means that even under compression, piston ring 5 can still tightly fit the gap between connecting rod 602 and cylinder 401 due to the controlled difference, without excessive deformation or slippage. By limiting the difference to within 0.85 times X, an appropriate gap is maintained to ensure airflow while maintaining good sealing performance.

[0162] Furthermore, the design of D2 directly affects the fixation and stability of piston ring 5. During system operation, piston ring 5 needs to withstand a certain compressive force; therefore, the diameter of D2 must be large enough to ensure that piston ring 5 does not detach from connecting rod 602 due to excessive clearance changes during compression. By controlling the difference between D4 and D2 within 0.85*X, slippage of piston ring 5 during compression can be effectively avoided.

[0163] Furthermore, piston ring 5 will undergo some deformation during compression, but this deformation must be within a reasonable range. The size of D2, by limiting the maximum clearance, ensures that the seal ring can still maintain its position on the piston rod when compressed, and will not fail or detach from the piston rod due to excessive compression.

[0164] Furthermore, L2-D4 = C2, where C2 ranges from 0mm to 1mm.

[0165] L2-D4=C2 represents the difference between the maximum diameter L2 of piston ring 5 and the inner diameter D4 of cylinder 401. In this design, when C2 is close to 1mm, it means that L2 (the diameter of piston ring 5) is approximately 1mm larger than D4 (the inner diameter of cylinder 401).

[0166] C2 = 1mm does not mean there is a gap. In fact, it means that the piston ring 5 is slightly larger than the cylinder 401. This ensures that during the compression process, the piston ring 5 can fit tightly against the inner wall of the cylinder 401, providing a sufficient sealing effect and preventing gas leakage during piston movement.

[0167] The piston ring 5 is designed to ensure that the piston can fit tightly against the inner wall of cylinder 401 during compression, forming a good seal. With L2 greater than D4 (i.e., C2 close to 1mm), the piston ring 5 is slightly larger than the inner diameter of cylinder 401. Thus, during operation, through a certain amount of compression or elastic deformation, the piston ring will come into tight contact with the cylinder wall, forming a sealing line, thereby preventing gas leakage.

[0168] Furthermore, D1≥L2-X:

[0169] Wherein, D1≥L2-X: To ensure that the piston ring 5 does not detach from the connecting rod 602 during operation, the diameter D1 of the first sealing disc 1301 needs to be greater than or equal to L2-X. This design allows the first sealing disc 13014 to provide reliable support for the piston ring 5, preventing the piston ring 5 from sliding or falling off during its movement within the cylinder 401, thereby ensuring a sealing effect.

[0170] Furthermore, D1 must be less than D2 to prevent collision between the first sealing disc 1301 and the cylinder 401 during compression.

[0171] During compression, a certain angle will form between connecting rod 602 and cylinder 401. If D1 is too large, it will cause connecting rod 602 (especially piston disc 6021) to collide with the inner wall of cylinder 401 when tilted, affecting the normal operation of cylinder 401. Therefore, the size of D1 must be controlled within a reasonable range to ensure both sealing effect and prevent mechanical interference.

[0172] In one specific embodiment, the inner diameter D4 of the cylinder 401 ranges from 10mm to 45mm.

[0173] The fifth embodiment of the present invention provides a portable air pump, and based on the previous embodiment, an airflow space 7 is formed between the second wall surface 102 and the eccentric wheel 601, and the air inlet port 4011 of the cylinder 401 is connected to the airflow space 7.

[0174] In this embodiment, an airflow space 7 is formed between the second wall 102 and the eccentric wheel 601. The airflow within the airflow space 7 is periodically disturbed by the rotation of the eccentric wheel 601. The rotation of the eccentric wheel 601 generates periodic pressure fluctuations, which effectively disturb the airflow, maintaining a relatively dynamic flow within the airflow space 7 and thus increasing the airflow velocity. After controlled disturbance, the airflow can flow more evenly and stably within the airflow space 7 and can flow to the intake port 4011 of the cylinder 401 in a shorter time. This disturbed airflow can enter the cylinder 401 more smoothly and quickly, improving intake efficiency.

[0175] In addition, external air can also enter the airflow space 7 through the gap in the housing 1 to replenish the gas supply. This allows the external air to flow more smoothly and merge with the already disturbed airflow after entering through the gap in the housing 1. This replenishment not only improves the stability of the airflow but also ensures a continuous air supply to the air intake port 4011, preventing insufficient air supply when the air intake is operating at high speed.

[0176] Since the airflow space 7 is directly connected to the air intake port 4011 of the cylinder 401, the airflow can quickly enter the cylinder 401 after being disturbed by the airflow space 7. In this way, the speed and fluidity of the airflow entering the cylinder 401 are greatly improved, avoiding the inflation delay problem caused by the slow air intake process. Especially in application scenarios that require rapid inflation, it can significantly improve the working efficiency of the air pump.

[0177] The sixth embodiment of the present invention provides a portable air pump, and based on the previous embodiment, the air pumping chamber 402 is located above the cylinder 401 in the height direction of the housing 1;

[0178] The air-inflating chamber 402 and the cylinder 401 are both located on one side of the second wall 102, and the axis of the air-inflating chamber 402 and the axis of the cylinder 401 are aligned with the height direction of the housing 1.

[0179] In this embodiment, the air-compressing chamber 402 is positioned above the cylinder 401. This arrangement allows gas to quickly enter the air-compressing chamber 402 for storage or output after the cylinder 401 completes gas compression, via a one-way valve or other flow-guiding structure. By placing the air-compressing chamber 402 above the cylinder 401, the gas flow path is effectively shortened, improving airflow efficiency. Furthermore, the connectivity between the cylinder 401 and the air-compressing chamber 402 is optimized, ensuring that gas can be rapidly transferred from the cylinder 401 to the air-compressing chamber 402 during piston movement, avoiding airflow stagnation and loss.

[0180] Both the air-inflating chamber 402 and the cylinder 401 are located on one side of the second wall 102 of the housing 1, and their axes are aligned with the height direction of the housing 1. This allows for a more compact and rational layout of the entire airflow chamber, achieving more efficient airflow guidance within a limited space. By arranging the airflow chamber along the height direction of the housing 1, the airflow channel becomes more direct and smooth, reducing airflow resistance within the chamber and improving inflation efficiency.

[0181] In traditional portable air pumps, the air pump chamber 402 is usually located on the side of the cylinder 401 or in other unsuitable positions, causing the gas to have to travel a long path after compression before being output, and potentially even resulting in poor flow. In this embodiment, by placing the air pump chamber 402 above the cylinder 401, the gas flow path is shortened, effectively improving output efficiency. Simultaneously, because gas compression and discharge are more direct and rapid, the impact of internal pressure changes on pump movement is reduced, further optimizing pump stability.

[0182] The seventh embodiment of the present invention provides a portable air pump, and based on the previous embodiment, the air pumping chamber 402 is provided with an air pumping port 4021;

[0183] Wherein, the axis of the air inlet 4021 is perpendicular to the axis of the air inlet 402;

[0184] The air inlet 4021 extends to the second wall surface 102.

[0185] In this embodiment, the air pumping chamber 402 has an air pumping port 4021, and the axis of the air pumping port 4021 is perpendicular to the axis of the air pumping chamber 402. In traditional air pump designs, the air pumping port 4021 is usually set parallel to or at an angle to the axis of the airflow chamber. Such a design may affect the smoothness and efficiency of airflow. By setting the axis of the air pumping port 4021 perpendicular to the axis of the air pumping chamber 402, the output direction of the airflow can be better matched with the airflow direction within the chamber, reducing the resistance when the airflow passes through bends and improving the output efficiency of the airflow.

[0186] The air inlet 4021 is not limited to the interior of the air chamber 402, but extends to the second wall 102 of the housing 1. This design allows the air inlet 4021 to be directly connected to the external environment and can be easily connected or docked with inflatable devices (such as wheels, air cushions, sports equipment, etc.). The air inlet 4021 extending to the second wall 102 effectively improves the applicability of the air pump, making it easier for users to inflate the pump and enhancing the user experience.

[0187] Because the axis of the air inlet 4021 is perpendicular to the axis of the air chamber 402, and the air inlet 4021 extends to the second wall 102, gas can flow out of the air chamber 402 more efficiently. Compared with the traditional design, this design reduces the resistance during airflow and avoids energy loss when the gas passes through a tortuous path, thereby improving the air pumping efficiency.

[0188] The eighth embodiment of the present invention provides a portable air pump, and based on the previous embodiment, the air pumping chamber 402 is provided with a detection port;

[0189] Wherein, the axis of the detection port is perpendicular to the axis of the air inlet 4021;

[0190] The detection port is connected to a detection cavity 8, and a pressure detection device 801 is installed inside the detection cavity 8.

[0191] In this embodiment, the air inflation chamber 402 has a detection port, the axis of which is perpendicular to the axis of the air inlet 4021. This avoids the air inlet 4021 and the detection port being positioned in the same direction, reducing interference between them and allowing the detection system to perform air pressure detection independently of the airflow path. This arrangement not only improves the accuracy of air pressure detection but also avoids interference with the detection device during airflow, thus improving the overall inflation stability.

[0192] The detection port is connected to a detection chamber 8, within which a pressure detection device 801 is installed. This pressure detection device 801 can detect the air pressure in the air pump in real time and feed the pressure data back to the control system via corresponding sensors or circuit modules. Through this real-time pressure detection device 801, the user can obtain the current inflation status at any time and adjust the inflation process based on the detection results.

[0193] By monitoring air pressure in real time, the air pump can adjust its operating status promptly, avoiding the risk of reduced inflation efficiency or equipment damage due to over-inflation or under-inflation. The air pressure detection device 801 works in conjunction with the air pump's control system to automatically adjust the operating status of the drive module 3, making the inflation process more efficient and precise. Simultaneously, the detection device provides real-time feedback, helping users understand the current inflation progress and avoiding excessively long operation times.

[0194] The ninth embodiment of the present invention provides a portable air pump, and based on the previous embodiment, the cylinder 401 and the air pumping chamber 402 are connected by a one-way flow guiding structure 9, the one-way flow guiding structure 9 comprising:

[0195] A valve plate 901 is disposed inside the air pumping chamber 402 and covers the communication port between the cylinder 401 and the air pumping chamber 402;

[0196] A sealing element 902 is disposed at the communication port and contacts the valve plate 901.

[0197] In this embodiment, the cylinder 401 and the air-inflating chamber 402 are connected by a unidirectional flow-guiding structure 9. This structure ensures that the airflow flows in only one direction, from the cylinder 401 into the air-inflating chamber 402, without flowing in the opposite direction.

[0198] The unidirectional flow structure 9 includes a valve plate 901 and a seal 902. The valve plate 901 is disposed inside the air-inflating chamber 402, covering the connection between the cylinder 401 and the air-inflating chamber 402. The function of the valve plate 901 is to control the unidirectional flow of air. When the air pressure in the cylinder 401 is high, the valve plate 901 opens, allowing air to flow from the cylinder 401 into the air-inflating chamber 402; when the air pressure changes, the valve plate 901 automatically closes to prevent air backflow. The seal 902 contacts the valve plate 901, enhancing the sealing between the valve plate 901 and the connection, ensuring that gas can only flow in one direction, avoiding leakage and unnecessary airflow loss.

[0199] The tenth embodiment of the present invention provides a portable air pump, and based on the previous embodiment, includes a display module 10, which is disposed on the first wall surface 101.

[0200] In this embodiment, the display module 10 is disposed on the first wall surface 101 of the portable air pump housing 1. This location makes the display module 10 easy for the user to observe, especially during inflation, allowing the user to easily monitor real-time air pressure changes and make corresponding adjustments. By being disposed on the first wall surface 101, the display module 10 can operate independently of other components, ensuring good visual effects and ease of operation.

[0201] The display module 10 displays key information such as current air pressure, inflation status, and remaining battery power in real time via a display screen or indicator lights. Specifically, the display module 10 includes:

[0202] Air pressure display: Displays the current air pressure value of the inflating device (such as tires, air cushions, etc.) in the form of numbers or charts, allowing users to clearly understand whether the set inflation standard has been reached.

[0203] Battery power display: Displays the remaining battery power of the battery module in real time, reminding users to charge the battery in time if the power is low during the inflation process, so as to avoid interruption.

[0204] Operating status prompts: For example, whether inflation is complete, whether the equipment has malfunctioned, or whether inspection or maintenance is required. The display module 10 provides users with clear and concise feedback through different colors or indicator lights.

[0205] By introducing the display module 10, users can not only monitor the inflation progress in real time when using the portable air pump, but also charge it in time according to the displayed battery level, avoiding interruption due to depletion of power. Furthermore, the real-time displayed air pressure information helps users avoid over-inflation or under-inflation, ensuring better inflation results. The display module 10 is particularly important in situations requiring precise inflation, allowing users to control the inflation process more accurately.

[0206] The eleventh embodiment of the present invention provides a portable air pump, which has at least the following features:

[0207] The design parameter H represents the numerical value of the air pump housing height;

[0208] The design parameter W represents the width of the air pump housing.

[0209] The design parameter L represents the numerical value of the length of the air pump housing;

[0210] The design parameter H is in the range of 60mm to 88mm.

[0211] The design parameter W has a range of 23mm to 35mm.

[0212] The design parameter L has a range of 39mm to 49mm.

[0213] Furthermore, the aforementioned design parameters H, W, and L can take any value within their respective ranges, which has the following properties:

[0214] The portable air pump can inflate the object to be inflated to pressure P;

[0215] Furthermore, the pressure P ranges from 105 psi to 150 psi;

[0216] The volume of the portable air pump's cylinder before compression is V1:

[0217]

[0218] The compressed volume is V2:

[0219]

[0220] And it satisfies:

[0221] 16≤V1 / V2≤60;

[0222] Where D4 is the inner diameter of the cylinder, K is the stroke of the cylinder, s is the clearance of the cylinder, t is the thickness of the air outlet, and d is the diameter of the air outlet.

[0223] In this embodiment, the design parameters H, W, and L of the portable air pump represent the height, width, and length of the air pump housing 1, respectively. Their specific value ranges are crucial to the portability and performance of the device. According to the provided design parameter ranges, H ranges from 60mm to 88mm, W ranges from 23mm to 35mm, and L ranges from 39mm to 49mm. This size setting makes the air pump both compact and easy to carry. Since this portable air pump is mainly intended for mobile use scenarios, such as cycling or sports, the reasonable design dimensions ensure that the product is lightweight and easy to store and operate.

[0224] Furthermore, the rationality of the design parameters is closely related to its compression ratio. The cylinder's volume V1 before compression and its volume V2 after compression must meet the compression ratio requirement of 16 ≤ V1 / V2 ≤ 60. This compression ratio has a significant impact on the motor load and the inflation effect. If the compression ratio is too high, it means that the gas is compressed more tightly in a small volume, making the compression of the gas in the cylinder more difficult, thereby increasing the burden on the motor, causing the motor to overload or overheat, affecting the stability and lifespan of the equipment. If the compression ratio is too low, it means that the gas is not fully compressed. Although the motor load is lighter, the output pressure will not be high enough to meet the high-pressure inflation requirements. Therefore, the inflation efficiency and actual use effect will be affected.

[0225] Therefore, this embodiment ensures that the motor operates under a reasonable load by limiting the range of V1 / V2, while also ensuring that the portable air pump can achieve the desired inflation pressure P (105psi to 150psi) while maintaining portability. This not only optimizes the motor's operating efficiency but also improves the overall performance of the portable air pump, making it able to meet the needs of high-pressure inflation without being too bulky or having excessive power, thus meeting practical usage requirements.

[0226] In one specific embodiment, the stroke of the cylinder is K, and satisfies:

[0227] K = 2 * Q, where Q is the eccentricity of the eccentric wheel of the portable air pump.

[0228] In one specific embodiment, the stroke K of the cylinder ranges from 8 mm to 12 mm. Preferably, the stroke K is 9 mm.

[0229] In a specific embodiment of the present invention, by limiting the cylinder stroke K to a range of 8mm to 12mm, the amount of gas compression during each inflation process can be precisely controlled. An appropriate stroke range effectively ensures that the gas is properly compressed within the cylinder, thereby achieving the predetermined inflation pressure. An excessively long stroke may result in a slow compression speed, affecting inflation efficiency, while an excessively short stroke may prevent the cylinder from fully compressing the gas, failing to achieve the required high-pressure inflation effect. A reasonable stroke maintains both inflation speed and ensures that the inflation pressure meets the user's needs.

[0230] Optimizing the cylinder stroke not only affects the air volume but also directly relates to the motor's workload. Limiting the stroke range to between 8mm and 12mm helps reduce the motor's load, preventing excessive strain on the motor under excessive stroke, and lowering the risk of overheating or failure. A well-designed stroke allows the motor to operate efficiently under lower loads, thereby improving overall efficiency and extending the motor's lifespan.

[0231] In one specific embodiment, the clearance s of the cylinder is in the range of 0.2mm to 0.5mm;

[0232] Furthermore, the clearance s refers to the width between the piston disc end face and the cylinder inner wall when the piston disc reaches its maximum compression position. Preferably, the clearance s is 0.2 mm.

[0233] In this embodiment, the proper design of the clearance s is crucial for the cylinder's sealing performance and gas compression efficiency. By controlling the clearance s within the range of 0.2mm to 0.5mm, it is possible to ensure good sealing of the piston disc during compression while avoiding gas leakage and reduced compression efficiency due to excessive clearance. An appropriate clearance ensures that the gas within the cylinder is fully compressed to achieve the expected charging pressure, while also helping to reduce internal cylinder friction and extend the equipment's service life.

[0234] In one specific embodiment, the diameter d of the air outlet of the cylinder ranges from 3mm to 4mm;

[0235] And / or, the thickness t of the air outlet of the cylinder is in the range of 0.5 mm to 3 mm.

[0236] In this embodiment, the diameter d and thickness t of the cylinder's air outlet directly affect the airflow. An appropriate outlet diameter ensures smooth gas flow from the cylinder during inflation, preventing excessive airflow resistance and reduced inflation efficiency. By controlling the diameter d between 3mm and 4mm, rapid and efficient gas flow is guaranteed, reducing airflow obstruction and increasing inflation speed. Simultaneously, a suitable thickness t (0.5mm to 3mm) ensures that the outlet, while allowing for smooth airflow, also guarantees sufficient strength and durability, preventing deformation or damage during high-pressure inflation.

[0237] The thickness of the vent hole plays a crucial role in the structural strength of the cylinder. An appropriate vent hole thickness enhances the cylinder's structural stability, ensuring that damage or deformation due to excessive pressure does not occur during prolonged use. Furthermore, a reasonable thickness design improves the vent hole's corrosion resistance, ensuring the air pump can operate stably for extended periods in various environments.

[0238] Furthermore, the design principle for thickness t is to minimize it to reduce clearance volume and improve compression efficiency. However, to meet the installation requirements of the front-end sealing ring and the minimum wall thickness requirements of the die-casting process in manufacturing, the thickness needs to be appropriately increased. Meanwhile, the diameter d has a significant impact on performance: a smaller diameter reduces the exhaust velocity and increases the operating current, while a larger diameter increases the clearance volume, leading to a slower inflation speed. Therefore, preferably, the diameter d is 3.5 mm and the thickness t is 1 mm.

[0239] In the description of the embodiments of the present invention, it should be understood that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "center", "top", "bottom", "top", "bottom", "inner", "outer", "inner side", "outer side", etc. indicate the orientation or positional relationship.

[0240] In the description of the embodiments of the present invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "assembly" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in the present invention based on the specific circumstances.

[0241] In the description of embodiments of the present invention, specific features, structures, materials or characteristics may be combined in any suitable manner in one or more embodiments or examples.

[0242] In the description of the embodiments of the present invention, it should be understood that "-" and "~" represent a range between two numerical values, and this range includes the endpoints. For example, "AB" represents a range greater than or equal to A and less than or equal to B. "A~B" represents a range greater than or equal to A and less than or equal to B.

[0243] In the description of embodiments of the present invention, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. Additionally, the character " / " in this document generally indicates that the preceding and following related objects have an "or" relationship.

[0244] Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A portable air pump, characterized in that, At least have: The design parameter H represents the numerical value of the air pump housing height; The design parameter W represents the width of the air pump housing. The design parameter L represents the numerical value of the length of the air pump housing; The design parameter H is in the range of 60mm to 88mm. The design parameter W has a range of 23mm to 35mm. The design parameter L has a range of 39mm to 49mm. Furthermore, the aforementioned design parameters H, W, and L can take any value within their respective ranges, which has the following properties: The portable air pump can inflate the object to be inflated to pressure P; Furthermore, the pressure P ranges from 105 psi to 150 psi; The volume of the portable air pump's cylinder before compression is V1: ; The compressed volume is V2: ; And it satisfies: 16≤V1 / V2≤60; Where D4 is the inner diameter of the cylinder, K is the stroke of the cylinder, s is the clearance of the cylinder, t is the thickness of the air outlet, and d is the diameter of the air outlet of the cylinder. case; The power module is disposed inside the housing and located on one side of the first wall; The drive module is located inside the housing and adjacent to the bottom surface of the housing; An airflow cavity is disposed inside the housing and located on one side of the second wall; The first wall surface and the second wall surface are two opposing side walls of the housing; Furthermore, the airflow cavity includes a cylinder and an air-inflating cavity; The cylinder and the air-inflating chamber are connected in one direction only; Furthermore, a piston ring is slidably connected inside the cylinder; The piston ring is connected to the drive module via a transmission component to generate piston movement within the cylinder; The air chamber has a height M1, and the cylinder has a height M2; Where M1+M2>1 / 2H, and M2≥M1.

2. The portable air pump according to claim 1, characterized in that, The stroke of the cylinder is K, and it satisfies: K = 2 * Q, where Q is the eccentricity of the eccentric wheel of the portable air pump.

3. The portable air pump according to claim 2, characterized in that, The stroke K of the cylinder is in the range of 8mm to 12mm.

4. The portable air pump according to claim 1, characterized in that, The clearance s of the cylinder is in the range of 0.2mm to 0.5mm; Furthermore, the clearance s refers to the width between the end face of the piston disc and the inner wall of the cylinder when the piston disc reaches the maximum compression position.

5. The portable air pump according to claim 1, characterized in that, The diameter d of the cylinder's air outlet is in the range of 3mm to 4mm. And / or, the thickness t of the air outlet of the cylinder ranges from 0.5 mm to 3 mm.

6. The portable air pump according to claim 1, characterized in that, Includes a connecting rod, the end of which is provided with a piston disc; An annular groove is formed along the circumferential wall of the piston disc; Furthermore, a piston ring is embedded in the annular groove; Wherein, along the connecting rod axis, the axial dimension of the annular groove is H1, and the axial dimension of the piston ring is X; M1-X=C1, where C1 ranges from 0.2mm to 2mm; An airflow channel is provided at the bottom of the annular groove; Furthermore, the piston disc is provided with a through airflow port, which corresponds to the position of the airflow groove.

7. The portable air pump according to claim 6, characterized in that, The piston disc includes a first sealing disc and a second sealing disc; The annular groove is located between the first sealing disc and the second sealing disc; Wherein, along the connecting rod radial direction, the maximum diameter of the first sealing disc is D1, the maximum diameter of the second sealing disc is D2, the maximum diameter of the outer ring surface of the piston ring is L2, and the inner diameter of the cylinder is D4; Where L2≥D4; D4>D2>D1.

8. The portable air pump according to claim 7, characterized in that, L2-D4=C2, where the value of C2 ranges from 0mm to 1mm; Furthermore, 0mm≤D4-D2≤0.85*X; Furthermore, D1≥L2-X.

9. The portable air pump according to claim 1, characterized in that, The air inflator chamber is equipped with a detection port; The detection port is connected to a detection cavity, and a pressure detection device is installed in the detection cavity. And / or, including a display module disposed within the housing.

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