Portable inflating pump

Abstract

The invention relates to a portable inflating pump, and belongs to the technical field of inflating pumps. The value range of a design parameter H is 60 mm to 88 mm; the value range of the design parameter W is 23 mm to 35 mm; the value range of the design parameter L is from 39 mm to 49 mm; the portable inflating pump can inflate an object to be inflated to the pressure P; the value range of the pressure P is from 105 psi to 150 psi; the volume of an air cylinder of the portable inflating pump before compression is V1, the volume of the air cylinder after compression is V2, and V1 / V2 is larger than or equal to 16 and smaller than or equal to 60. It is guaranteed that the inflation pump is small enough in size and convenient to carry and store, and exertion of the inflation function of the inflation pump is not affected. By reasonably controlling the compression ratio, the motor can efficiently work under low load, the inflation efficiency is improved, and the service life of the motor is prolonged.

Description

Technical Field

[0001] The invention belongs to the technical field of air pumps, and relates to a technology for optimizing the air flow path of an air pump, and in particular to a portable air pump. Background Art

[0002] Portable air pumps are widely used to inflate sports equipment, especially in emergency or outdoor environments. Portable air pumps are small and easy to carry, making them a common inflatable device. With the improvement of living standards and the increase of personalized needs, the market demand for portable air pumps is gradually increasing, and users are also increasingly demanding their performance, efficiency, convenience, etc.

[0003] However, there is often a certain contradiction between the performance and portability of portable air pumps in the prior art. Due to the need to provide high-pressure inflation capabilities, the design size of the air pump is often large, which makes it difficult for the size and weight of the device to be small enough, affecting its portability. At the same time, the compression ratio of the cylinder is directly related to the inflation effect and the motor load. If the compression ratio of the cylinder is designed too high, the workload required for gas compression increases, and the motor is overloaded, which can easily lead to overheating or overload, affecting the durability and stability of the equipment; if the compression ratio is too low, high-pressure inflation cannot be achieved, and the inflation efficiency decreases, which may not be able to meet the high-pressure requirements in actual use. Therefore, how to ensure that the portable air pump has good portability, stability and high efficiency while ensuring the inflation pressure and efficiency is a major challenge in current technical design. Summary of the invention

[0004] In order to solve the above-mentioned problems in the prior art, the present invention provides a portable air pump.

[0005] In order to achieve the above object, the technical solution adopted by the present invention is:

[0006] Provided is a portable air pump having at least:

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

[0008] The design parameter W represents the numerical value of the width of the air pump housing;

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

[0010] Wherein, the value range of the design parameter H is: 60mm to 88mm;

[0011] The value range of the design parameter W is: 23mm to 35mm;

[0012] The value range of the design parameter L is: 39mm to 49mm;

[0013] Moreover, the aforementioned design parameter H, design parameter W, and design parameter L can take any value within their corresponding value ranges:

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

[0015] Furthermore, the pressure P has a value range of 105 psi to 150 psi;

[0016] Among them, the volume of the cylinder of the portable air pump before compression is V1:

[0017]

[0018] The volume after compression is V2:

[0019]

[0020] And satisfy:

[0021] 16≤V1 / V2≤60;

[0022] Among them, 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 outlet hole, and d is the diameter of the cylinder outlet hole.

[0023] The stroke of the cylinder is K, and 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 ranges from 8 mm to 12 mm.

[0026] Preferably, the clearance s of the cylinder has a value range of: 0.2 mm to 0.5 mm;

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

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

[0029] And / or, the thickness t of the air outlet of the cylinder ranges from 0.5 mm to 3 mm.

[0030] Preferably, it includes:

[0031] case;

[0032] A power module is arranged inside the housing;

[0033] A driving module is disposed inside the housing and is electrically connected to the power module;

[0034] Cylinder and pumping chamber;

[0035] The cylinder and the pumping cavity are in one-way communication.

[0036] Preferably, it comprises a connecting rod, the end of which is provided with a piston disc;

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

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

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

[0040] M1-X=C1, the value range of C1 is 0.2mm to 2mm;

[0041] An air flow groove, arranged at the bottom of the annular groove;

[0042] Furthermore, the piston disc is provided with a through air flow opening corresponding to the position of the air flow groove.

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

[0044] Wherein, the annular groove is located between the first sealing disk and the second sealing disk;

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

[0046] Among them, L2≥D4; D4>D2>D1.

[0047] Preferably, L2-D4=C2, and the value range of C2 is 0mm-1mm;

[0048] And, 0mm≤D4-D2≤0.85*X;

[0049] And, D1≥L2-X.

[0050] Preferably, an airflow space is formed between the second wall surface and the eccentric wheel, and the air inlet port of the cylinder is communicated with the airflow space.

[0051] Preferably, the inflation cavity is provided with an inflation port.

[0052] Preferably, the inflation cavity is provided with a detection port;

[0053] Wherein, the detection port is connected to a detection cavity, and an air pressure detection device is arranged in the detection cavity.

[0054] Preferably, the cylinder and the pumping chamber are connected via a one-way flow guiding structure, and the one-way flow guiding structure comprises:

[0055] A valve sheet is disposed in the pumping cavity and covers the communication port between the cylinder and the pumping cavity;

[0056] A sealing member is arranged at the communication port and contacts the valve plate.

[0057] Preferably, a display module is included, and the display module is arranged on the housing.

[0058] The present invention provides a portable air pump, and the beneficial effects of the present invention are embodied in:

[0059] The portable air pump of the present invention significantly improves the performance and user experience of the device by reasonably setting the value range of the design parameters H, W, and L and optimizing the cylinder compression ratio. This ensures that the air pump is small enough to be convenient to carry and store, and does not affect the performance of its inflation function. This makes the air pump of the present invention more flexible in actual use, and users can easily put it into small spaces such as cars and backpacks for easy use at any time.

[0060] The compression ratio V1 / V2 of the cylinder is set between 16 and 60, avoiding the negative effects of too high or too low compression ratios. A moderate compression ratio ensures efficient compression of the gas during the inflation process, while effectively reducing the load on the motor. Too high a compression ratio will cause the motor to be overloaded, affecting the life and stability of the motor, while too low a compression ratio will result in poor inflation and failure to achieve the expected high-pressure output. By reasonably controlling the compression ratio, the present invention enables the motor to operate efficiently under a lower load, improves inflation efficiency, and extends the service life of the motor. BRIEF DESCRIPTION OF THE DRAWINGS

[0061] Figure 1 A three-dimensional diagram of the portable air pump provided by the present invention;

[0062] Figure 2 A side view of the portable air pump provided by the present invention;

[0063] Figure 3 A rear view of the portable air pump provided by the present invention;

[0064] Figure 4 A top view of the portable air pump provided by the present invention;

[0065] Figure 5 A front view of the portable air pump provided by the present invention;

[0066] Figure 6 This is one of the structural diagrams of the hidden housing of the portable air pump proposed by the present invention;

[0067] Figure 7 This is the second structural diagram of the hidden housing of the portable air pump proposed by the present invention;

[0068] Figure 8 A cross-sectional view of the portable air pump provided by the present invention;

[0069] Fig. 9 A three-dimensional diagram of the cylinder in the portable air pump proposed by the present invention;

[0070] Fig.10 for Fig. 9 a cross-sectional view of the structure shown;

[0071] Fig.11 This is a front view of a connecting rod in a portable air pump provided by the present invention;

[0072] Fig.12 for Fig.11 a cross-sectional view of the structure shown;

[0073] Fig.13 This is a stereoscopic view of the connecting rod of the portable air pump proposed by the present invention.

[0074] Description of reference numerals:

[0075] 1. Shell; 101. First wall; 102. Second wall; 2. Power module; 3. Drive module; 401. Cylinder; 4011. Inlet port; 402. Pumping cavity; 4021. Pumping port; 5. Piston ring; 6. Transmission member; 601. Eccentric wheel; 602. Connecting rod; 6021. Piston disc; 6022. Annular groove; 7. Air flow space; 8. Detection cavity; 801. Air pressure detection device; 9. One-way flow guide structure; 901. Valve plate; 902. Sealing member; 10. Display module; 11. Air flow groove; 12. Air flow port; 1301. First sealing disc; 1302. Second sealing disc. DETAILED DESCRIPTION

[0076] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0077] See also Figure 1 - Fig.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 of a portable air pump, including:

[0079] Shell 1;

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

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

[0082] The height direction of the power module 2 is consistent with the height direction of the housing 1, and the axis direction of the driving module 3 is consistent with the length direction of the housing 1;

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

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

[0085] Wherein, the axis of the airflow cavity is consistent with the height direction of the housing 1;

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

[0087] The cylinder 401 and the pumping chamber 402 are in one-way communication;

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

[0089] The piston ring 5 is connected to the driving module 3 via a transmission member 6 to form a piston movement in the cylinder 401;

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

[0091] Among them, M1+M2>1 / 2H, and M2≥M1;

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

[0093] In this embodiment, the shell 1 serves as the outer frame of the entire air pump, providing the necessary structural support and fixing of the internal components. Moreover, the shell 1 does not have an obvious air intake structure, i.e., an air inlet. External air enters the interior of the shell 1 through the installation gap of the shell 1. Thus, compared with the traditional portable air pump design, the prior art usually requires a specially designed air inlet or air inlet valve to guide the external air in. However, this embodiment reduces the requirements for the guiding structure of the external air by eliminating the significant air inlet design, thereby simplifying the structure of the entire device and the number of internal components. By utilizing the installation gap of the shell 1 as an air intake channel, not only the manufacturing cost is reduced, but also the failure points are reduced, thereby improving the reliability of the device. Although there is no explicit air inlet, this embodiment ensures the stability and controllability of the air inflow by controlling the installation gap of the shell 1. Moreover, it can also prevent impurities, dust, etc. from entering the interior of the device, protect the internal components, and extend the service life of the device.

[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 driving module 3.

[0095] The driving module 3 is located near the bottom of the housing 1, and the axial direction is consistent with the length direction of the housing 1. The driving module 3 includes an electric motor, which converts electrical energy into mechanical energy through a transmission member 6 to drive the piston to move.

[0096] The airflow cavity is arranged on one side of the second wall surface 102 of the shell 1, and the axis is consistent with the height direction of the shell 1. The airflow cavity includes a cylinder 401 and an air pumping cavity 402, which are connected by a one-way connecting structure to ensure that the gas can only flow from the cylinder 401 to the air pumping cavity 402 to avoid gas backflow.

[0097] In the prior art, the cylinder 401 of the portable air pump is usually directly connected to the air inlet 4021, that is, the cylinder 401 is connected to the pressure inside the tire. As the pressure inside the tire gradually increases, the pressure that the cylinder 401 needs to overcome increases, resulting in a significant increase in the energy required for the piston to move, which leads to the following problems:

[0098] When the cylinder 401 is directly connected to the inflation port 4021, as the air pressure continues to rise, the pressure inside the tire will be directly transmitted to the piston cavity. This means that the piston must overcome increasing external pressure during each compression process. As the pressure increases, the driving force required for the movement of the piston will also increase. In order to overcome these external pressures, the drive module 3 needs to consume more energy. Under this structural form, the air pump has low energy efficiency, especially when facing high-pressure inflation requirements, which often leads to excessive work of the drive module 3, thereby affecting the service life and inflation efficiency of the equipment.

[0099] Since cylinder 401 is directly affected by the internal pressure of the tire, the movement of the piston requires greater force for compression. This situation will result in a reduction in the amount of air flow during each compression process, while the inflation time will be extended and the inflation efficiency will be significantly reduced. In addition, the piston moves frequently and consumes a lot of energy. Within a certain period of time, the device cannot provide sufficient airflow and pressure, which affects the user experience, especially in scenarios where high-pressure inflation is required.

[0100] During high-pressure inflation, the pressure of the cylinder 401 and the internal pressure of the tire directly interact with each other, increasing the workload of the drive module 3, especially in the later stage of the inflation process. In order to overcome the high pressure, the drive module 3 needs to provide a greater power output, which may lead to the risk of overload and even shorten the service life of the drive module 3.

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

[0102] Specifically, after the inflation cavity 402 is added, the cylinder 401 and the inflation port 4021 are no longer directly connected, but the airflow is buffered and regulated through the inflation cavity 402. The inflation cavity 402 is equivalent to providing an additional air storage space for the airflow, so that the airflow has undergone a certain pressure adjustment when entering the inflation port 4021, avoiding the cylinder 401 directly facing the drastic changes in the internal pressure of the tire. In this way, the pressure that needs to be overcome during the movement of the piston will be reduced, thereby reducing the power consumption of the drive module 3 and improving the inflation efficiency.

[0103] The piston ring 5 is installed inside the cylinder 401 and is slidably connected to the inner wall of the cylinder 401. The piston ring 5 is connected to the driving module 3 through the transmission member 6 to form a piston movement.

[0104] On the basis of the above, due to the optimized layout of the power module 2 and the drive module 3, the space of nearly half of the height inside the housing 1 can be occupied by the airflow cavity. This layout optimization not only increases the volume of the airflow cavity, but also makes the cylinder 401 have a larger effective working space, thereby significantly improving the overall performance of the portable air pump.

[0105] Specifically, the cylinder 401 has a longer working stroke and a larger volume, so that each piston movement can accommodate more air flow and provide a higher air pressure output. Compared with the low efficiency caused by space limitations and short piston stroke in the traditional technology, this structure fully utilizes the space in the housing 1, so that the height of the airflow cavity is effectively expanded.

[0106] By increasing the volume of cylinder 401 and optimizing the airflow path, the portable air pump can provide 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 and achieve higher output pressure to meet more complex inflation needs. Whether it is inflation under high pressure or application scenarios that require stable airflow output, it can achieve better performance.

[0107] The optimized layout of the power module 2 and the drive module 3 makes the design of the entire portable air pump more compact. The space inside the housing 1 is effectively utilized, which can ensure sufficient airflow cavity volume without adding extra volume and weight. This structure enables the portable air pump to have more efficient performance while maintaining a small size, meeting the dual needs of modern users for portability and efficiency.

[0108] In addition, it is further found that, in the portable air pump, under the condition that the power of the power module 2 and the driving module 3 is limited, the height of the piston chamber is not necessarily as high as possible, because:

[0109] As the height of the cylinder 401 increases, the piston stroke becomes longer, which means that more air needs to be compressed and inhaled each time the piston moves. This will cause the drive module 3 to require more power support each time it moves. If the cylinder 401 is too high and the required power exceeds the output capacity of the power module 2, then even if the battery or power module 2 can provide enough power, it may not be possible to achieve an efficient inflation process due to insufficient power. This will cause the device to operate unstable, or even fail to reach the desired pressure.

[0110] Although a taller cylinder 401 can increase the air flow rate per movement, if the piston stroke is too long, it may lead to a waste of energy. Due to the limited power of the power module 2 and the drive module 3, when the height of the cylinder 401 is too large, the piston may not be able to fully and effectively utilize the energy of each movement. Long-term movement and higher gas flow will lead to energy loss, thereby reducing the inflation efficiency of the device. An excessively long piston stroke will result in limited efficiency and air pressure increase of each airflow, thereby extending the inflation time and increasing the power consumption of the device.

[0111] Based on this, in order to find the best balance between ensuring the efficiency and power limitation of the portable air pump, the present invention optimizes its performance by limiting the height of the air cylinder 401 and the air pumping chamber 402. Specifically, the height of the air cylinder 401 and the air pumping chamber 402 is limited mainly to ensure that the device can efficiently complete the inflation task under power limitation while avoiding excessive energy consumption or increasing the burden on the device.

[0112] In the embodiment of the present invention, the height of the cylinder 401 and the pumping chamber 402 is defined as:

[0113] M1+M2>1 / 2H, wherein M1 is the height of the inflation cavity 402 , M2 is the height of the cylinder 401 , and H is the height of the shell 1 .

[0114] Meanwhile, M2≥M1, that is, the height of the cylinder 401 should be greater than or equal to the height of the pumping cavity 402, to ensure that the compression amount of the piston is sufficient but does not excessively increase the total volume of the airflow cavity.

[0115] Thereby, it is possible to ensure that the amount of air compression in each piston movement is sufficient, while avoiding excessive power consumption and inefficient charging caused by an overly high cylinder 401.

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

[0117] Eccentric wheel 601 and connecting rod 602;

[0118] The eccentric wheel 601 is connected to the driving end of the driving 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] Wherein, 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 member 6 includes an eccentric wheel 601 and a connecting rod 602. The eccentric wheel 601 is connected to the driving end of the driving module 3 (referring to the motor), and the other end of the connecting rod 602 drives the piston ring 5 to generate piston movement through the rotation of the eccentric wheel 601. The eccentric structure of the eccentric wheel 601 makes the piston movement regular and stable, and can effectively control the compression and suction process of the piston, thereby improving the stability of the airflow and the pumping efficiency.

[0122] On the basis of the above, the present 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 arranged above the eccentric wheel 601. Since the housing 1 of the present embodiment has no significant air inlet, the external air can only enter the interior through the gap of the housing 1. When the eccentric wheel 601 rotates, the rotation of the eccentric wheel 601 will generate air flow disturbance inside the housing 1, so that the air flow is disturbed at the gap of the housing 1 and accelerates to flow toward the cylinder 401.

[0123] The rotation of the eccentric wheel 601 forms airflow disturbance through its eccentric structure. This airflow disturbance can effectively avoid the phenomenon of static airflow or inefficient air intake, so that air can enter the cylinder 401 more smoothly.

[0124] Through the disturbance of the eccentric wheel 601, the external air is better supplemented, ensuring that the cylinder 401 can inhale air stably and sufficiently during the intake stage.

[0125] like Figures 9 to 13 As shown, the third embodiment of the present invention provides 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 provided along the circumferential wall surface of the piston disc 6021;

[0127] Furthermore, the piston ring 5 is movably embedded in 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, thereby avoiding the problem of gas leakage. The annular groove 6022 allows the seal 902 to maintain a stable sealing state during the movement of the piston, thereby ensuring the effective compression and transmission of the gas in the cylinder 401. The piston ring 5 is configured to be able to slide and displace along the height direction of the annular groove 6022, allowing the seal 902 to more flexibly adapt to changes in the cavity during the movement of the piston. The setting of the sliding displacement reduces friction, improves the smoothness and efficiency of the piston during movement, and avoids wear or blocking caused by the fixation of the seal 902.

[0129] Wherein, along the axial direction 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, the value range of C1 is 0.2mm-2mm;

[0131] The air flow groove 11 is provided at the bottom of the annular groove 6022;

[0132] Furthermore, the piston disc 6021 is provided with a through air flow opening 12 corresponding to the position of the air flow groove 11 .

[0133] In this embodiment, an annular groove 6022 is provided on the circumferential wall surface of the piston disc 6021, and a piston ring 5 is installed in the groove. The design of the annular groove 6022 allows the piston ring 5 to have a certain degree of freedom in the groove. Unlike the traditional fixed sealing ring or leather cup design, the piston ring 5 can be slightly moved and adjusted during the reciprocating motion of the piston. This design makes the piston ring 5 no longer rely on close contact with the inner wall of the cylinder 401 to achieve air intake, but guides air into the cylinder 401 through the air flow groove 11 provided in the annular groove 6022 and the air flow port 12 on the piston disc 6021, thereby ensuring that sufficient air intake can be maintained in the miniaturized cylinder 401.

[0134] When the piston returns, the connecting rod 602 and the piston disc 6021 are displaced in the return direction, and the piston ring 5 is displaced in the annular groove 6022 in the opposite direction to the return direction due to the friction with the inner wall of the cylinder 401. At this time, the air flow groove 11 is completely exposed and is located in the outer area of ​​the cylinder 401, so that the air can smoothly enter the cylinder 401 through the air flow groove 11 and the air flow port 12 to quickly replenish the air. This design does not rely on the deformation of the piston ring 5 or the gap with the inner wall of the cylinder 401, and effectively avoids the problem of insufficient air intake under miniaturization conditions. As the piston returns, the piston ring 5 readjusts its position after the friction disappears, partially covering the air flow groove 11, and preparing to enter the next compression stroke.

[0135] On the basis of the above, it is further found that the larger the intake volume is, the better. Too large intake volume will increase the airflow resistance, which will cause many problems of the motor (as described in the background technology). Therefore, it is further proposed that along the axis direction 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;

[0136] H1-X=C1, the value range of C1 is 0.2mm-2mm.

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

[0138] When C1 is too large, the gap between the annular groove 6022 and the piston ring 5 is too large, which will cause the sealing effect of the piston ring 5 to deteriorate, and the gas will easily leak from the gap, reducing the working efficiency of the system.

[0139] Too large a C1 will make the flow velocity and pressure distribution uneven, causing fluctuations in the air intake, leading to unstable operation of the motor and affecting overall performance. Due to gas leakage, the system needs to consume more power to maintain the airflow, which in turn increases the burden and energy consumption of the motor and reduces the efficiency of the equipment.

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

[0141] Too small a gap leads to frequent mechanical contact between the piston ring 5 and the annular groove 6022, increasing friction, causing increased wear of parts, and affecting the sliding performance and life of the piston. Due to insufficient air intake and increased air flow resistance, the motor will face a higher load, which will cause the motor to overheat or be damaged.

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

[0143] This difference will neither cause excessive airflow to increase airflow resistance nor affect system efficiency due to insufficient air intake, thereby achieving balance and control of air intake. Reasonable clearance makes the airflow have moderate resistance when passing through the annular groove 6022, which can maintain a stable air intake of the system and avoid excessive airflow turbulence, ensuring stable motor load. The appropriate difference can effectively reduce the friction between the piston ring 5 and the annular groove 6022, reduce parts wear, and extend the service life of the equipment. This design can reduce energy consumption while ensuring the accuracy of airflow control and improving the operating efficiency of the entire system.

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

[0145] In addition, the size of the piston ring 5 and the annular groove 6022 is matched so that during the movement of the connecting rod 602, the air intake path is optimized and the air intake volume is precisely controlled. This not only improves the working efficiency of the air pump, but also helps to achieve a miniaturized design of the device and meet the needs of portable applications. At the same time, the appropriate size of the piston ring 5 can also enhance the sealing effect, reduce air leakage, and further reduce the energy consumption of the motor.

[0146] In summary, by reasonably setting the axial dimension ratio of the piston ring 5 and the annular groove 6022, this embodiment successfully solves the problems of increased air flow resistance and excessive motor load caused by excessive air intake, and improves 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] Wherein, the annular groove 6022 is located between the first sealing disk 1301 and the second sealing disk 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 and intake air volume on the basis of a certain air leakage and intake air 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 second sealing disc 1302 is designed to control the sealing of the intake air volume and air leakage volume, rather than complete sealing. This design helps to achieve efficient 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 to ensure that the intake air 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 intake process, air can smoothly enter the air flow groove 11 under controlled conditions. This gap regulates the intake air volume, enabling sufficient air volume to be inhaled each time the piston returns, ensuring that the air pump can achieve an efficient 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 disk 1302 is not completely sealed, which can avoid the problem of restricted air intake caused by complete sealing. By allowing part of the airflow to enter from the gap between the second sealing disk 1302 and the inner wall of the cylinder 401, the smooth flow of the airflow is guaranteed, and the backlog of air during the compression process is effectively avoided. This control seal design can accurately adjust the amount of leakage to a certain extent, ensuring that the air can fully enter the cylinder 401 during the intake process, but can provide sufficient sealing effect during the compression process to reduce unnecessary air leakage. Such a balanced design controls the amount of leakage while ensuring the intake volume, making the equipment operation more stable.

[0157] Since the clearance design of the second sealing disk 1302 can ensure the smooth flow of air intake, the motor does not need to run frequently to make up for the problem of insufficient air intake during operation, thereby significantly reducing the idle consumption of the motor. In addition, this design also avoids the phenomenon of incomplete compression caused by air obstruction, ensuring that the motor can operate efficiently in each working cycle.

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

[0159] Furthermore, 0mm≤D4-D2≤0.85*X:

[0160] The difference between the inner diameter D4 of the cylinder 401 and the diameter D2 of the second sealing disk 1302 can be 0, that is, in the tightest fit, the diameter of the second sealing disk 1302 is equal to the inner diameter of the cylinder 401. This tight fit helps to achieve an excellent sealing effect, especially when the system is working at high pressure, it can minimize gas leakage.

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

[0162] In addition, the design of D2 directly affects the fixation and stability of the piston ring 5. During the operation of the system, the piston ring 5 needs to withstand a certain compression force, so the diameter of D2 must be large enough to ensure that the piston ring 5 will not be separated from the connecting rod 602 due to excessive clearance changes during compression. By controlling the difference of D4-D2 within 0.85*X, the piston ring 5 can be effectively prevented from slipping during the compression process.

[0163] The piston ring 5 will deform to a certain extent when compressed, but this deformation must be within a reasonable range. The size of D2 limits the maximum gap to ensure that when the seal ring is compressed, it can still maintain its position on the piston rod and will not fail or detach from the piston rod due to excessive compression.

[0164] Furthermore, L2-D4=C2, and the value range of C2 is 0mm-1mm:

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

[0166] C2=1 mm does not mean there is a gap, but actually 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 to prevent gas leakage when the piston moves.

[0167] The purpose of designing the piston ring 5 is to ensure that the piston can be in close contact with the inner wall of the cylinder 401 during compression and inflation to form a good seal. When L2 is larger than D4 (i.e., when C2 is close to 1 mm), the piston ring 5 is slightly larger than the inner diameter of the cylinder 401. In this way, during operation, through a certain compression or elastic deformation, the piston ring will be in close contact with the cylinder wall to form a sealing line, thereby preventing gas leakage.

[0168] Furthermore, D1 ≥ L2-X:

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

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

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

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

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

[0174] In this embodiment, an airflow space 7 is formed between the second wall 102 and the eccentric wheel 601. The airflow in the airflow space 7 is affected by the rotation of the eccentric wheel 601 and is disturbed periodically. When the eccentric wheel 601 rotates, periodic pressure fluctuations are generated, which can effectively disturb the airflow, so that it maintains a relatively dynamic fluidity in the airflow space 7, thereby increasing the flow speed of the airflow. After the airflow is disturbed in a controlled manner, it can flow more evenly and stably in the airflow space 7, and can flow to the air intake port 4011 of the cylinder 401 in a shorter time. This disturbed airflow can enter the cylinder 401 more smoothly and quickly, thereby improving the air intake efficiency.

[0175] In addition, external air can also enter the airflow space 7 through the gap of the shell 1 to replenish gas, so that after entering through the gap of the shell 1, the external air can flow more smoothly and merge with the already disturbed airflow. This replenishment effect not only improves the stability of the airflow, but also ensures that the air source of the air inlet port 4011 is continuous, avoiding the situation where the air inlet port is short of air when working at high speed.

[0176] Since the airflow space 7 is directly connected to the air inlet 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 the application scenario where fast inflation is required, which 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, in the height direction of the shell 1, the air pump cavity 402 is located above the cylinder 401;

[0178] The air pumping cavity 402 and the cylinder 401 are both located on one side of the second wall surface 102 , and the axis of the air pumping cavity 402 and the axis of the cylinder 401 are consistent with the height direction of the shell 1 .

[0179] In this embodiment, the pumping chamber 402 is arranged above the cylinder 401. This layout allows the gas to quickly pass through the one-way valve or other flow-guiding structures into the pumping chamber 402 for storage or output after the cylinder 401 completes gas compression. By placing the pumping chamber 402 above the cylinder 401, the flow path of the gas can be effectively shortened and the efficiency of airflow transmission can be improved. Furthermore, the connectivity between the cylinder 401 and the pumping chamber 402 is optimized, ensuring that during the movement of the piston, the gas can be quickly transferred from the cylinder 401 to the pumping chamber 402, avoiding airflow retention and loss.

[0180] The air pumping cavity 402 and the cylinder 401 are both arranged on one side of the second wall surface 102 of the shell 1, and their axes are consistent with the height direction of the shell 1. The layout of the entire airflow cavity can be made more compact and reasonable, and more efficient airflow guidance can be achieved in a limited space. By arranging the airflow cavity along the height direction of the shell 1, the airflow channel is made more direct and smooth, reducing the flow resistance of the air in the cavity and improving the air pumping efficiency.

[0181] In a conventional portable air pump, the air pumping chamber 402 is usually arranged on the side of the cylinder 401 or in other unreasonable positions, which results in the gas having to pass through a longer path before it can be discharged after being compressed, and may even cause poor flow. However, in this embodiment, by arranging the air pumping chamber 402 above the cylinder 401, the flow path of the gas is shortened and the output efficiency is effectively improved. At the same time, since the compression and discharge of the gas are more direct and rapid, the influence of the change of the internal pressure on the movement of the pump body is reduced, and the stability of the pump body is further optimized.

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

[0183] The axis of the pumping port 4021 is perpendicular to the axis of the pumping cavity 402;

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

[0185] In this embodiment, the pumping cavity 402 is provided with a pumping port 4021, and the axis of the pumping port 4021 is perpendicular to the axis of the pumping cavity 402. In the traditional air pump design, the pumping port 4021 is usually arranged parallel to the axis of the airflow cavity or at a certain angle, and such a design may affect the smoothness and efficiency of the airflow. By arranging the axis of the pumping port 4021 perpendicularly to the axis of the pumping cavity 402, the output direction of the airflow can be better matched with the flow direction of the airflow in the cavity, reducing the resistance of the airflow when passing through the turning point, and improving the output efficiency of the airflow.

[0186] The air inlet 4021 is not limited to the interior of the air inlet cavity 402, but extends to the second wall 102 of the shell 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 equipment (such as wheels, air cushions, sports equipment, etc.). The air inlet 4021 extending to the second wall 102 can effectively improve the applicability of the air pump, allowing users to more conveniently perform inflation operations when using it, thereby improving the user experience of the product.

[0187] Since the axis of the air inlet 4021 is perpendicular to the axis of the air inlet cavity 402, and the air inlet 4021 extends to the second wall 102, the gas can flow out of the air inlet cavity 402 more efficiently. Compared with the traditional design, this design reduces the resistance of the air flow, avoids the energy loss of the gas when passing through the tortuous path, and thus improves the air inlet efficiency.

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

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

[0190] The detection port is connected to a detection cavity 8, and an air pressure detection device 801 is arranged in the detection cavity 8.

[0191] In this embodiment, the inflation cavity 402 is provided with a detection port, the axis of which is perpendicular to the axis of the inflation port 4021. This can avoid the inflation port 4021 and the detection port being arranged in the same direction, reduce interference between the two, and enable 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 the airflow passing through, and improves the overall inflation stability.

[0192] The detection port is connected to a detection cavity 8, and an air pressure detection device 801 is arranged in the detection cavity 8. The air pressure detection device 801 can detect the air flow pressure in the air pump in real time, and feed back the air pressure data to the control system through the corresponding sensor or circuit module. Through this real-time air pressure detection device 801, the user can obtain the current inflation state at any time and adjust the inflation process according to the detection result.

[0193] By monitoring the air pressure in real time, the air pump can adjust its working state in time, avoiding the risk of reduced inflation efficiency or damage to the equipment due to over-inflation or insufficient inflation. The air pressure detection device 801 is used in conjunction with the control system of the air pump to automatically adjust the operating state of the drive module 3, making the inflation process more efficient and accurate. At the same time, the detection device can also provide real-time feedback to help users understand the current inflation progress in time and avoid prolonged operation.

[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 pump cavity 402 are connected through a one-way flow guide structure 9, and the one-way flow guide structure 9 includes:

[0195] The valve plate 901 is disposed in the pumping cavity 402 and covers the communication port between the cylinder 401 and the pumping cavity 402;

[0196] The sealing member 902 is disposed at the communication port and is in contact with the valve plate 901 .

[0197] In this embodiment, the cylinder 401 and the pumping cavity 402 are connected by a one-way flow guide structure 9. This structure ensures that the airflow flows in only one direction, from the cylinder 401 into the pumping cavity 402, and does not flow in the opposite direction.

[0198] The one-way flow guide structure 9 includes a valve plate 901 and a sealing member 902. The valve plate 901 is arranged in the air pumping cavity 402, covering the connecting port between the cylinder 401 and the air pumping cavity 402. The valve plate 901 is used to control the one-way 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 pumping cavity 402; and when the air pressure changes, the valve plate 901 automatically closes to prevent air from flowing back. The sealing member 902 contacts the valve plate 901, enhancing the sealing between the valve plate 901 and the connecting port, ensuring that the gas can only flow in a single direction, and avoiding leakage and unnecessary air flow loss.

[0199] The tenth embodiment of the present invention provides a portable air pump, and based on the previous embodiment, comprises a display module 10 , wherein the display module 10 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 position selection makes the display module 10 easy for the user to observe, especially during the inflation process, the user can easily monitor the real-time air pressure changes and make corresponding adjustments. By being disposed on the first wall surface 101, the display module 10 can be independent of other components, ensuring good visual effects and convenient operation.

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

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

[0203] Battery power display: Real-time display of the remaining power of the battery module, reminding the user that if the power is low during the inflation process, they can charge it in time to avoid downtime.

[0204] Working status prompt: for example, whether the inflation is complete, whether the equipment is faulty, whether it needs inspection or maintenance, etc. Through different colors or indicator lights, the display module 10 can provide the user with concise and clear feedback.

[0205] By introducing the display module 10, when using the portable air pump, the user can not only understand the inflation progress in real time, but also charge in time according to the displayed power prompt to avoid stopping midway due to power exhaustion. In addition, the real-time displayed air pressure information can help the user avoid over-inflation or under-inflation, ensuring a better inflation effect. Especially in some precise inflation occasions, the role of the display module 10 is particularly important, allowing the user to control the inflation process more accurately.

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

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

[0208] The design parameter W represents the numerical value of the width of the air pump housing;

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

[0210] Wherein, the value range of the design parameter H is: 60mm to 88mm;

[0211] The value range of the design parameter W is: 23mm to 35mm;

[0212] The value range of the design parameter L is: 39mm to 49mm;

[0213] Moreover, the aforementioned design parameter H, design parameter W, and design parameter L can take any value within their corresponding value ranges:

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

[0215] Furthermore, the pressure P has a value range of 105 psi to 150 psi;

[0216] Among them, the volume of the cylinder of the portable air pump before compression is V1:

[0217]

[0218] The volume after compression is V2:

[0219]

[0220] And satisfy:

[0221] 16≤V1 / V2≤60;

[0222] Among them, 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 outlet hole, and d is the diameter of the cylinder outlet hole.

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

[0224] Looking further, the rationality of the design parameters is closely related to its compression ratio. The volume V1 of the cylinder before compression and the volume V2 after compression meet the compression ratio requirement of 16≤V1 / V2≤60. This compression ratio has an important 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, which makes the compression of the gas in the cylinder more difficult, thereby increasing the burden on the motor, causing the motor to overload or overheat, and affecting the stability and life of the equipment. If the compression ratio is too low, it means that the gas is not fully compressed. Although the burden on the motor is lighter, it will also cause the output pressure to be not high enough to meet the needs of high-pressure inflation. 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, and also ensures that the portable air pump can reach the desired inflation pressure P (105psi to 150psi) while maintaining portability. This not only optimizes the operating efficiency of the motor, but also improves the overall performance of the portable air pump, so that it can meet the needs of high-pressure inflation without being too bulky or overpowered, and meets actual use requirements.

[0226] In a specific implementation, 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 a specific implementation, 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 stroke K of the cylinder within the range of 8 mm to 12 mm, the amount of gas compression during each inflation process can be accurately controlled. An appropriate stroke range can effectively ensure that the gas is reasonably compressed in the cylinder, thereby reaching a predetermined inflation pressure. A stroke that is too long may cause the compression speed of the cylinder to be too slow, affecting the inflation efficiency, while a stroke that is too short may cause the cylinder to fail to fully compress the gas and fail to achieve the desired high-pressure inflation effect. Through a reasonable stroke, the inflation speed can be maintained while ensuring that the inflation pressure meets user needs.

[0230] The optimization of the cylinder stroke not only affects the inflation volume, but is also directly related to the motor's workload. The stroke range is limited to between 8mm and 12mm, which helps to reduce the load on the motor, avoid excessive burden on the motor under excessive stroke, and reduce the risk of motor overheating or failure. The moderate stroke design allows the motor to operate efficiently under lower loads, thereby improving overall work efficiency and extending the life of the motor.

[0231] In a specific embodiment, the clearance s of the cylinder has a value range of: 0.2 mm to 0.5 mm;

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

[0233] In this embodiment, the proper design of the clearance s is crucial to the sealing of the cylinder and the gas compression efficiency. By controlling the clearance s within the range of 0.2 mm to 0.5 mm, it is possible to ensure that the piston disc maintains good sealing during the compression process, while avoiding gas leakage and reduced compression efficiency caused by excessive clearance. The appropriate clearance can ensure that the gas in the cylinder is fully compressed to achieve the expected inflation pressure, and also helps to reduce friction in the cylinder and extend the service life of the equipment.

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

[0235] And / or, the thickness t of the air outlet of the cylinder ranges from 0.5 mm to 3 mm.

[0236] In this embodiment, the diameter d and thickness t of the cylinder air outlet directly affect the fluidity of the airflow. An appropriate air outlet diameter can ensure that the gas flows out of the cylinder smoothly during the inflation process, and avoid excessive resistance to the airflow, which leads to reduced inflation efficiency. By controlling the diameter d between 3mm and 4mm, it can ensure that the gas flows out quickly and efficiently, reduce airflow blockage, and increase the inflation speed. At the same time, a reasonable choice of thickness t (0.5mm to 3mm) can ensure that the air outlet has sufficient strength and durability while satisfying smooth airflow, and avoid deformation or damage during high-pressure inflation.

[0237] The thickness design of the air outlet plays an important role in the structural strength of the cylinder. Appropriate thickness of the air outlet can enhance the structural stability of the cylinder and ensure that it will not be damaged or deformed due to excessive pressure during long-term use. In addition, reasonable thickness design can also improve the corrosion resistance of the air outlet, ensuring that the air pump can operate stably for a long time in various environments.

[0238] Furthermore, the design principle of the thickness t is to minimize it to reduce the clearance volume and improve the compression efficiency. However, in order to meet the installation requirements of the front-end sealing ring and the minimum wall thickness requirements of the die-casting process in production, the thickness needs to be appropriately increased. At the same time, the size of the diameter d has a significant impact on the performance: a reduction in diameter will reduce the gas outlet speed and increase the operating current, while an increase in diameter will increase the clearance volume, resulting in a slower inflation speed. Based on this, preferably, the value of the diameter d is 3.5mm and the value of the thickness t is 1mm.

[0239] In the description of the embodiments of the present invention, it needs to be understood that terms such as “up”, “down”, “front”, “back”, “left”, “right”, “vertical”, “horizontal”, “center”, “top”, “bottom”, “top”, “bottom”, “inside”, “outside”, “inside”, and “outside” indicate orientation or positional relationships.

[0240] In the description of the embodiments of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "install", "connect", "connect", and "assemble" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0241] In the description of the embodiments of the present invention, specific features, structures, materials or characteristics may be combined in a suitable manner in any 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 values, and the 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 the embodiments of the present invention, the term "and / or" herein is merely a description of the association relationship of associated objects, indicating that three relationships may exist. For example, A and / or B may represent: A exists alone, A and B exist at the same time, and B exists alone. In addition, the character " / " herein generally indicates that the associated objects before and after are in an "or" relationship.

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

Claims

1. A portable air pump, characterized in that: At least: The design parameter H represents the height of the air pump housing; The design parameter W represents the numerical value of the width of the air pump housing; The design parameter L representing the numerical value of the air pump housing length; Wherein, the value range of the design parameter H is: 60mm to 88mm; The value range of the design parameter W is: 23mm to 35mm; The value range of the design parameter L is: 39mm to 49mm; Moreover, the aforementioned design parameter H, design parameter W, and design parameter L can take any value within their corresponding value ranges: The portable air pump can inflate the object to be inflated to a pressure of P; Furthermore, the pressure P has a value range of 105 psi to 150 psi; Among them, the volume of the cylinder of the portable air pump before compression is V1: The volume after compression is V2: And satisfy: 16≤V1 / V2≤60; Among them, 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 outlet hole, and d is the diameter of the cylinder outlet hole.

2. The portable air pump according to claim 1, characterized in that: The stroke of the cylinder is K, and 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 has a value range of 8 mm to 12 mm.

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

5. The portable air pump according to claim 1, characterized in that: The diameter d of the air outlet of the cylinder has a value range of: 3 mm to 4 mm; 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 any one of claims 1 to 5, characterized in that: include: case; A power module is arranged inside the housing; A driving module is disposed inside the housing and is electrically connected to the power module; Cylinder and pumping chamber; The cylinder and the pumping cavity are in one-way communication.

7. The portable air pump according to claim 6, characterized in that: It comprises a connecting rod, the end of which is provided with a piston disc; An annular groove is provided along the circumferential wall surface of the piston disc; Furthermore, a piston ring is embedded in the annular groove; Wherein, along the connecting rod axis direction, the axial dimension of the annular groove is H1, and the axial dimension of the piston ring is X; M1-X=C1, the value range of C1 is 0.2mm to 2mm; An air flow groove, arranged at the bottom of the annular groove; Furthermore, the piston disc is provided with a through air flow opening corresponding to the position of the air flow groove.

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

9. The portable air pump according to claim 8, characterized in that: L2-D4=C2, the value range of C2 is 0mm-1mm; And, 0mm≤D4-D2≤0.85*X; And, D1≥L2-X.

10. The portable air pump according to claim 6, characterized in that: The inflation cavity is provided with a detection port; Wherein, the detection port is connected to a detection cavity, and an air pressure detection device is arranged in the detection cavity; And / or, comprising a display module, wherein the display module is arranged on the housing.

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