Piston rod and inflating pump

Abstract

The invention relates to a piston rod and an inflating pump, and belongs to the technical field of inflating pumps. Comprising piston rods and piston discs, the piston rod and the piston disc are integrally formed; an annular groove is formed in the circumferential wall face of the piston disc. The annular groove is sleeved with the piston ring, the piston ring is in clearance fit with the annular groove, the axial size of the annular groove is H1, and the axial size of the piston ring is X; h < 1-X > is equal to C1, and the value range of C1 is 0.2 mm to 2 mm; the airflow groove is formed in the groove bottom of the annular groove; the piston disc is provided with a through airflow opening which corresponds to the airflow groove in position. Therefore, the piston ring does not depend on close contact with the inner wall of the piston cavity to achieve air inflow, air is guided into the piston cavity through the air flow groove formed in the annular groove and the air flow opening in the piston disc, and therefore it is guaranteed that enough air inflow can be maintained in the small piston cavity.

Description

Technical Field

[0001] The invention belongs to the technical field of air pumps, and relates to a technology for increasing the air intake volume in a miniaturized air pump, and in particular to a piston rod and an air pump. Background Art

[0002] In portable applications, miniaturized air pumps can provide users with a lighter and more convenient use experience. Traditional air pumps are large in size and heavy in weight, so they are not suitable for carrying around or using for a long time. Miniaturized air pumps can not only reduce the size and weight of the equipment, but also optimize the internal structure, reduce unnecessary components and complexity, thereby improving the flexibility of use and market competitiveness of the equipment. Therefore, miniaturization of air pumps is not only a market demand, but also the direction of technological progress of air pumps.

[0003] However, the problem faced by miniaturization of air pumps is that the power of the motor will inevitably be reduced. This means that if the air intake is too much, the piston rod will be subject to greater air flow resistance during the inflation stage. For low-power motors, this may have the following effects: When the air pump is compressing air, if the air flow resistance is too large, the low-power motor will need to overcome a greater reaction force to push the piston rod and piston disc to work. In this case, the load on the motor will increase significantly. Since the torque output of a low-power motor is limited, when the load exceeds its rated power range, the motor may overheat, slow down, or even stop running. In the case of increased air flow resistance, the low-power motor may not be able to maintain its normal operating speed. This will cause the air pump to displace less air in each compression cycle, thereby reducing the overall pumping efficiency. Especially in situations where large capacity or high pressure is required, a miniaturized air pump may not achieve the expected inflation effect, and the use time will be greatly extended, affecting the user experience.

[0004] When the motor load approaches or exceeds its rated power, the motor consumes more energy to maintain operation. However, due to the limited power reserve of low-power motors themselves, when the airflow resistance is large, the mismatch between the motor's energy consumption and the actual effect produced will be more obvious. This increase in power loss will not only affect the continuous working ability of the air pump, but also accelerate the wear and aging of the motor. Therefore, for miniaturized air pumps, how to find the best balance between airflow resistance and motor output power is a crucial issue. Summary of the invention

[0005] In order to solve the above-mentioned problems in the prior art, the present invention provides a piston rod and an air pump.

[0006] In order to achieve the above object, the technical solution adopted by the present invention is: A piston rod is provided, comprising: Piston rod and piston disc; The piston rod and the piston disc are integrally formed; Wherein, the circumferential wall surface of the piston disc forms an annular groove; A piston ring is sleeved on the annular groove and has a clearance fit with the annular groove; Wherein, along the axial direction of the piston rod, the axial dimension of the annular groove is H1, and the axial dimension of the piston ring is X; H1-X=C1, the value range of C1 is 0.2mm-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.

[0007] Preferably, 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 piston 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 piston cylinder is D4; Among them, L2≥D4; D4>D2>D1.

[0008] Preferably, L2-D4=C2, and the value range of C2 is 0mm-1mm; And, 0mm≤D4-D2≤0.85*X; And, D1≥L2-X.

[0009] Preferably, the inner cavity diameter D4 of the piston cylinder ranges from 10 mm to 45 mm.

[0010] Preferably, the distance between the inner ring surface of the piston ring and the bottom of the annular groove is L3; Moreover, the value range of L3 is 0mm to Xmm.

[0011] Preferably, in the radial direction of the piston rod, the cross-sectional area of ​​the annular groove is S2, and the total projected area of ​​the airflow groove on the same cross-section is S1; Moreover, 0.05≤S1 / S2≤0.3.

[0012] Preferably, the piston ring has a circular cross-section and is made of elastic material.

[0013] Preferably, the axis A of the piston rod is non-coaxial with the center point P of the piston disc.

[0014] Preferably, the piston rod has a connecting end B1 and a connecting end B2; Wherein, the connecting end B1 is connected to the piston disc; Wherein, the connection end B2 is used to connect with the driving member.

[0015] The present invention also provides an air pump, comprising: A piston rod as described in any of the above technical solutions.

[0016] The present invention provides a piston rod and an air pump, and the beneficial effects of the present invention are as follows: The design of the annular groove allows the piston ring to have a certain degree of freedom in the groove. Unlike the traditional fixed sealing ring or leather cup design, the piston ring can move and adjust slightly during the reciprocating motion of the piston. This design makes the piston ring no longer rely on close contact with the inner wall of the piston cavity to achieve air intake, but guides air into the piston cavity through the air flow groove set in the annular groove and the air flow port on the piston plate, thereby ensuring that sufficient air intake can be maintained in the miniaturized piston cavity. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 This is one of the schematic diagrams of the assembly of the piston rod and the piston chamber proposed by the present invention; Figure 2 This is the second schematic diagram of the assembly of the piston rod and the piston chamber proposed by the present invention; Figure 3 for Figure 1 a cross-sectional view of the structure shown; Figure 4 for Figure 3 A local enlarged schematic diagram of the structure shown at position E; Figure 5 A front view of the piston rod provided by the present invention; Figure 6 for Figure 5 a cross-sectional view of the structure shown; Figure 7 A top view of the piston rod provided by the present invention; Figure 8 A three-dimensional diagram of the piston rod proposed by the present invention; Fig. 9 A front view of the piston rod provided by the present invention; Fig.10 This is one of the three-dimensional diagrams of the air pump provided by the present invention; Fig.11 The second stereoscopic diagram of the air pump provided by the present invention; Fig.12 A cross-sectional view of the air pump provided by the present invention; Fig.13This is a schematic diagram of the cross-sectional area ratio of the airflow groove and the annular groove in the piston rod proposed by the present invention.

[0018] Description of reference numerals: 1. Piston rod; 2. Piston disc; 201. First sealing disc; 202. Second sealing disc; 3. Annular groove; 4. Piston ring; 5. Air flow groove; 6. Air flow port; 7. Piston cavity; 8. Air pump; 801. Housing; 802. Driving member; 803. Eccentric wheel mechanism; 804. Battery. DETAILED DESCRIPTION

[0019] 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.

[0020] See also Figures 1 to 13 As shown, the specific embodiments provided by the present invention are as follows: like Figures 1 to 5 As shown, the first embodiment of the present invention provides a piston rod, comprising: Piston rod 1 and piston disc 2; The piston rod 1 and the piston disc 2 are integrally formed; Wherein, the circumferential wall surface of the piston disc 2 forms an annular groove 3; The piston ring 4 is sleeved on the annular groove 3 and has a clearance fit with the annular groove 3; Wherein, along the axial direction of the piston rod 1, the axial dimension of the annular groove 3 is H1, and the axial dimension of the piston ring 4 is X; H1-X=C1, the value range of C1 is 0.2mm-2mm; An air flow groove 5 is provided at the bottom of the annular groove 3; Furthermore, the piston disc 2 is provided with a through air flow opening 6 corresponding to the position of the air flow groove 5 .

[0021] In this embodiment, the piston ring 4 is significantly different from the sealing ring or rubber ring in the prior art because: The sealing ring in the prior art mainly focuses on improving the sealing performance, so there are great restrictions on its degree of freedom. The sealing ring is usually fixedly embedded in the sealing groove to ensure that when the piston rod 1 moves, the sealing ring will not cause loose sealing due to shaking or displacement. Although this design can ensure the sealing effect, its degree of freedom in the piston chamber 7 is limited and cannot adapt to various working conditions. Especially in the miniaturized air pump 8, this fixed sealing ring is prone to increase friction between moving parts and affect the intake efficiency.

[0022] Moreover, the piston ring 4 of this embodiment is also significantly different from the leather cup in the prior art because: First, the air intake method of the leather cup in the prior art relies on the tiny gap between its edge and the inner wall of the piston chamber 7. When the piston rod 1 is in the return stroke, the gap between the edge of the leather cup and the inner wall of the piston chamber 7 expands, and air enters the piston chamber 7 through this gap. However, this air intake method has significant limitations in the miniaturization process, because after the diameter of the piston chamber 7 is reduced, the gap between the edge of the leather cup and the inner wall of the piston chamber 7 becomes smaller, and the air circulation is restricted, resulting in insufficient air intake.

[0023] Secondly, the air intake of the leather cup in the prior art is limited by the edge gap and the elastic properties of the leather cup material. This means that when the diameter of the piston cavity 7 and the size of the leather cup become smaller, the air intake decreases accordingly, and it is difficult to maintain a stable air inflow. Especially in the miniaturized air pump 8, the deformation space of the leather cup is limited, resulting in poor air intake effect.

[0024] Third, as the air pump 8 is miniaturized, the size and structure of the leather cup must be reduced accordingly. However, since the air intake method of the leather cup depends on its deformation, its air intake efficiency is easily reduced during the miniaturization process. In the miniaturized air pump 8, the air intake channel between the edge of the leather cup and the inner wall of the piston chamber 7 becomes narrower, and the air intake is insufficient, resulting in motor idle loss and low efficiency.

[0025] It should be noted that, for the miniaturized air pump 8, motor idle consumption is an extremely serious problem. The reasons are: During the operation of the air pump 8, the main task of the motor is to drive the piston to reciprocate, thereby sucking in air and compressing it. If the intake air volume is sufficient, the energy of the motor driving the piston each time will be effectively converted into the compressed kinetic energy of the air, thereby achieving an efficient working cycle.

[0026] However, when the air intake is insufficient (for example, when the cup design is limited in the miniaturized air pump 8), the amount of air sucked in each working cycle is reduced. This means that the motor cannot achieve the expected compression effect each time it drives the piston to move, resulting in reduced working efficiency. The motor frequently runs without fully utilizing its energy, consuming a large amount of electrical energy but failing to achieve the expected inflation effect, which results in motor idle consumption.

[0027] In order to maintain lightness and portability, the power of the motor of the miniaturized air pump 8 is usually designed to be smaller to avoid the increase of the device volume and weight. In this way, the load capacity and speed of the motor when running will be limited.

[0028] In the miniaturized design, since the size of the piston chamber 7 and the piston is reduced, the deformation space of the leather cup or the piston ring 4 is also reduced, so that the traditional air intake method cannot provide enough air. When the air intake is reduced, the power of the motor is forced to be further limited, because even if the motor is running, its energy cannot be effectively used - the motor does not have enough air to compress. In this way, most of the output power of the motor is consumed in idling, and no effective working output can be generated.

[0029] Therefore, since the motor needs more working cycles to reach the set pressure or air volume when the air intake is insufficient, this directly leads to a waste of electric energy. In the case of limited power supply (such as battery 804), the endurance of the small air pump 8 is significantly reduced.

[0030] When the motor is idling and running at high frequency, a large amount of heat will accumulate inside it. In particular, the miniaturized air pump 8 has limited heat dissipation conditions, and the motor is prone to overheating, which not only increases the risk of damage, but also accelerates the aging of the motor and other key components.

[0031] Under the miniaturized design, the power of the motor is already limited. If the air intake is insufficient and results in idle consumption, the motor must work longer or even start and stop frequently to achieve the desired effect. This is not only time-consuming, but also greatly affects the inflation efficiency of the equipment, making the working performance of the small air pump 8 far less than expected.

[0032] In general, when the air intake of the miniaturized air pump 8 is insufficient, it not only causes idle consumption of the motor, but also further amplifies the negative impact of idle consumption due to the limitation of the motor power by the miniaturized design itself. The motor runs in a continuously inefficient state, the energy consumption of the equipment increases, and the overheating and noise problems are aggravated, which ultimately seriously affects the use effect and life of the air pump 8.

[0033] Based on the above problems, this embodiment provides a structure of an annular groove 3 and a piston ring 4 to achieve efficient air intake in a miniaturized air pump 8, specifically: In this embodiment, an annular groove 3 is provided on the circumferential wall surface of the piston disc 2, and a piston ring 4 is installed in the groove. The design of the annular groove 3 allows the piston ring 4 to have a certain degree of freedom in the groove. Unlike the traditional fixed sealing ring or leather cup design, the piston ring 4 can move and adjust slightly during the reciprocating motion of the piston. This design makes the piston ring 4 no longer rely on close contact with the inner wall of the piston cavity 7 to achieve air intake, but guides air into the piston cavity 7 through the air flow groove 5 provided in the annular groove 3 and the air flow port 6 on the piston disc 2, thereby ensuring that sufficient air intake can be maintained in the miniaturized piston cavity 7.

[0034] When the piston returns, the piston rod 1 and the piston disc 2 are displaced in the return direction, and the piston ring 4 is displaced in the annular groove 3 in the opposite direction to the return direction due to the friction between the piston ring 4 and the inner wall of the piston chamber 7. At this time, the airflow groove 5 is completely exposed and is located in the outer area of ​​the piston chamber 7, so that the air can smoothly pass through the airflow groove 5 and the airflow port 6 into the piston chamber 7 for rapid air replenishment. This design does not rely on the deformation of the piston ring 4 or the gap with the inner wall of the piston chamber 7, and effectively avoids the problem of insufficient air intake under miniaturization conditions. As the piston returns, the piston ring 4 readjusts its position after the friction disappears, partially covering the airflow groove 5, and preparing to enter the next compression stroke.

[0035] On the basis of the above, it is further found that the larger the air intake volume is, the better it is. Too large an air intake volume will increase the air flow 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 piston rod 1, the axial dimension of the annular groove 3 is H1, and the axial dimension of the piston ring 4 is X; H1-X=C1, the value range of C1 is 0.2mm-2mm.

[0036] In this example, it was found that: When C1 is too large, the gap between the annular groove 3 and the piston ring 4 is too large, which will cause the sealing effect of the piston ring 4 to deteriorate, and the gas will easily leak from the gap, reducing the working efficiency of the system.

[0037] 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.

[0038] When C1 is too small, the gap between the piston ring 4 and the annular groove 3 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.

[0039] Too small a gap leads to frequent mechanical contact between the piston ring 4 and the annular groove 3, 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.

[0040] 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: This difference will neither increase the airflow resistance due to excessive airflow nor affect the system efficiency due to insufficient air intake, thereby achieving the balance and control of the air intake. A reasonable gap makes the airflow have moderate resistance when passing through the annular groove 3, which can not only maintain the stable air intake of the system, but also avoid excessive airflow turbulence and ensure the stability of the motor load. The appropriate difference can effectively reduce the friction between the piston ring 4 and the annular groove 3, reduce the wear of parts, and extend the service life of the equipment. This design can ensure the accuracy of airflow control while reducing energy consumption, and improve the operating efficiency of the entire system.

[0041] 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.

[0042] In addition, the size of the piston ring 4 and the annular groove 3 is matched so that during the movement of the piston rod 1, 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 the miniaturization design of the equipment and meet the needs of portable applications. At the same time, the appropriate size of the piston ring 4 can also enhance the sealing effect, reduce air leakage, and further reduce the energy consumption of the motor.

[0043] In summary, by reasonably setting the axial dimension ratio of the piston ring 4 and the annular groove 3, 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.

[0044] like Figure 5 As shown, in a specific embodiment, the axial dimension H1 of the annular groove 3 ranges from 2 mm to 3.5 mm. Preferably, the axial dimension H1 of the annular groove 3 is one of 2 mm, 2.5 mm, 3 mm, and 3.5 mm.

[0045] On the one hand, in the miniaturized air pump 8, the space is limited, and any structural design needs to be compact and efficient. The axial dimension H1 of the annular groove 3 determines the degree of freedom and movement space of the piston ring 4 in the groove.

[0046] If the annular groove 3 is too narrow, the freedom of the piston ring 4 is restricted and it cannot produce sufficient displacement during the return stroke, which will affect the complete exposure of the air flow groove 5, resulting in obstruction of the intake path, which is not conducive to improving the intake efficiency.

[0047] On the contrary, if the annular groove 3 is too wide, the piston ring 4 may shake too much in the groove, which not only increases friction and noise, but also easily causes gas leakage due to poor sealing, and more importantly, causes a significant increase in the intake volume. Therefore, in the miniaturized design, the axial size of the annular groove 3 must be selected to ensure compactness while ensuring that the piston ring 4 has enough room for movement, so as to maintain a balance between the miniaturization of the equipment and the intake volume.

[0048] In the miniaturized air pump 8, since the diameter and length of the piston chamber 7 are reduced, the length of the airflow groove 5 must also be optimized within the limited space. The axial dimension H1 of the annular groove 3 determines the effective length range of the airflow groove 5, so that it can provide sufficient flow channels for air in a compact structure. This optimized design ensures that in the miniaturized air pump 8, despite the reduced size, the airflow groove 5 can still provide sufficient air intake area, thereby improving the overall air intake efficiency.

[0049] On the other hand, the displacement of the piston ring 4 is determined by the axial dimension H1 of the annular groove 3. During the piston return stroke, the displacement of the piston ring 4 needs to be large enough to ensure that the air flow groove 5 is completely exposed and thus opened to the maximum extent. This design is particularly important in the miniaturized piston chamber 7, because only by ensuring the displacement of the piston ring 4 in a limited space can the intake efficiency be guaranteed.

[0050] In the range of 2 mm to 3.5 mm in the axial dimension of the annular groove 3, the displacement of the piston ring 4 is optimized to ensure that the airflow groove 5 is fully exposed during the return stroke, so that the air can quickly enter the piston cavity 7 through the airflow groove 5. This optimized displacement ensures that under miniaturization conditions, even if the diameter of the piston cavity 7 is small, sufficient air intake can still be maintained, avoiding the decrease in efficiency due to space reduction.

[0051] like Figure 5 As shown, in a specific embodiment, the axial dimension X of the piston ring 4 ranges from 1 mm to 2.5 mm.

[0052] like Figure 6 As shown, in a specific embodiment, the piston disc 2 includes a first sealing disc 201 and a second sealing disc 202; Wherein, the annular groove 3 is located between the first sealing disk 201 and the second sealing disk 202; Wherein, along the radial direction of the piston rod 1, the maximum diameter of the first sealing disk 201 is D1, the maximum diameter of the second sealing disk 202 is D2, the maximum diameter of the outer ring surface of the piston ring 4 is L2, and the inner diameter of the piston cylinder is D4; Among them, L2≥D4; D4>D2>D1.

[0053] In this embodiment, it is ensured that the structure of the piston disc 2 can provide a progressive sealing effect in a limited space (it should be noted that the sealing here does not mean complete sealing, but means that the leakage and intake are controlled on the basis of a certain amount of leakage and intake). Specifically: D1 < D2: This relationship indicates that the diameter of the second sealing disk 202 is slightly larger than the diameter of the first sealing disk 201. The purpose of this design is that when the piston rod 1 moves in the piston chamber 7, the design of the second sealing disk 202 tends to control the air intake and air leakage, rather than completely seal. This design helps to achieve efficient air intake in the miniaturized air pump 8 while maintaining reasonable airflow regulation. Specifically: A certain gap is left between the second sealing disc 202 and the inner wall of the piston chamber 7, allowing the airflow to enter the airflow groove 5 through this gap. This design is intended to control the air entry path and ensure that the air intake is optimized. The existence of this gap allows the air to enter the airflow groove 5 through the gap between the second sealing disc 202 and the inner wall of the piston chamber 7 during the piston return stroke, and enter the piston chamber 7 through the airflow port 6, thereby achieving air replenishment. In this way, during the entire piston return stroke, the airflow path is controlled rather than being completely blocked.

[0054] Of course, the gap size between the second sealing disk 202 and the inner wall of the piston chamber 7 can be precisely designed to ensure that during the intake process, the air can smoothly enter the air flow groove 5 under a controlled state. This gap adjusts the intake volume, so that each time the piston returns, sufficient air can be inhaled, ensuring that the air pump 8 can achieve an efficient intake effect.

[0055] This design avoids the problem of air flow obstruction in the traditional fully sealed design, and optimizes the amount of air flow entering by controlling the gap, thereby improving the working efficiency of the air pump 8 under miniaturized conditions.

[0056] In this embodiment, the second sealing disk 202 is not completely sealed, so that the problem of restricted air intake caused by complete sealing can be avoided. By allowing part of the airflow to enter from the gap between the second sealing disk 202 and the inner wall of the piston chamber 7, 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 leakage to a certain extent, ensuring that the air can fully enter the piston chamber 7 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 leakage while ensuring the intake volume, making the equipment operation more stable.

[0057] Since the clearance design of the second sealing disk 202 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.

[0058] Furthermore, due to the relationship of L2 ≥ D4, the outer ring surface of the piston ring 4 can contact the inner wall of the piston cylinder more closely, thereby providing a better sealing effect during the compression process.

[0059] Furthermore, 0mm ≤ D4 - D2 ≤ 0.85 * X: The difference between the inner diameter D4 of the piston cylinder and the diameter D2 of the second sealing disk 202 can be 0, that is, in the tightest fit, the diameter of the second sealing disk 202 is equal to the inner diameter of the piston cylinder. This tight fit helps to achieve an excellent sealing effect, especially when the system is working at high pressure, it can minimize gas leakage.

[0060] 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 4. This means that even if the piston ring 4 is in a compressed state, due to the control of the difference, the piston ring 4 can still fit tightly in the gap between the piston rod 1 and the piston cylinder 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.

[0061] In addition, the design of D2 directly affects the fixation and stability of the piston ring 4. During the operation of the system, the piston ring 4 needs to withstand a certain compression force, so the diameter of D2 must be large enough to ensure that the piston ring 4 will not be separated from the piston rod 1 due to excessive gap changes during compression. By controlling the difference between D4 and D2 within 0.85 * X, the piston ring 4 can be effectively prevented from slipping during the compression process.

[0062] The piston ring 4 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.

[0063] Furthermore, L2-D4=C2, and the value range of C2 is 0mm-1mm: L2 - D4 = C2 represents the difference between the maximum diameter L2 of the piston ring 4 and the inner diameter D4 of the piston barrel. In this design, when C2 is close to 1 mm, it means that L2 (the diameter of the piston ring 4) is about 1 mm larger than D4 (the inner diameter of the piston barrel).

[0064] C2 = 1mm does not mean there is a gap. It actually means that the piston ring 4 is slightly larger than the piston cylinder. This ensures that during the compression process, the piston ring 4 can fit tightly against the inner wall of the piston cylinder, providing a sufficient sealing effect to prevent gas leakage when the piston moves.

[0065] The purpose of the design of the piston ring 4 is to ensure that the piston can be tightly attached to the inner wall of the piston cylinder when compressing and inflating, forming a good seal. When L2 is larger than D4 (that is, when C2 is close to 1mm), the piston ring is slightly larger than the inner diameter of the piston cylinder. In this way, during operation, through a certain compression or elastic deformation, the piston ring will tightly contact the cylinder wall to form a sealing line, thereby preventing gas leakage.

[0066] Furthermore, D1 ≥ L2-X: Wherein, D1 ≥ L2 - X: In order to ensure that the piston ring 4 does not separate from the piston rod 1 during operation, the diameter D1 of the first sealing disk 201 needs to be greater than or equal to L2 - X. This design enables the first sealing disk 201 to provide reliable support for the piston ring, preventing the piston ring 4 from sliding or falling off during movement in the cylinder, thereby ensuring the sealing effect.

[0067] Furthermore, D1 must be smaller than D2 in order to prevent collision between the first sealing disk 201 and the piston cylinder during compression.

[0068] During the compression process, a certain angle is formed between the piston rod 1 and the piston cylinder. If D1 is too large, the piston rod 1 (especially the piston disc 2) will collide with the inner wall of the piston cylinder when tilted, affecting the normal operation of the piston cylinder. Therefore, the size of D1 must be controlled within a reasonable range to ensure the sealing effect and prevent mechanical interference.

[0069] In a specific embodiment, the inner diameter D4 of the piston cylinder ranges from 10 mm to 45 mm.

[0070] like Figure 6As shown, in a specific embodiment, the distance between the inner ring surface of the piston ring 4 and the bottom of the annular groove 3 is L3; Moreover, the value range of L3 is 0mm to Xmm.

[0071] In the prior art, the piston plate 2 and the piston rod 1 are usually connected in a hinged manner. Although this design can provide a certain degree of freedom, it has many problems in practical applications. In contrast, this embodiment adopts an integrally formed design, and by increasing L3 (the distance between the inner ring surface of the piston ring 4 and the bottom of the annular groove 3), the advantages of this integrally formed structure are further optimized.

[0072] Specifically, the articulated design relies on the flexibility of the joints to achieve the freedom of the piston disc 2, and these joints are prone to wear during long-term high-speed reciprocating motion. As wear increases, the matching accuracy of the joints decreases, resulting in excessive clearance or looseness during the movement of the piston disc 2, which in turn affects the sealing performance of the entire piston chamber 7.

[0073] In addition, in the miniaturized air pump 8, the space for joint design is limited, and the size and strength of the joint components are restricted. This may cause the joint to fatigue prematurely under frequent operation, increase the maintenance requirements of the equipment, and reduce the service life.

[0074] In addition, the articulated form requires additional components such as pins, bushings or connecting blocks, which increases the complexity of manufacturing. In addition, during the assembly process, the joint parts need to be precisely matched to ensure that they have sufficient flexibility and stability at high speeds.

[0075] In the miniaturized air pump 8, this complex assembly process not only increases the manufacturing cost, but may also lead to improper joint assembly due to size limitations, thereby affecting the overall performance and reliability of the device.

[0076] More importantly, the hinged form causes a certain angle deviation or swing of the piston disc 2 during movement, and this instability easily leads to inconsistent sealing effects between the piston disc 2 and the inner wall of the piston chamber 7. Especially in miniaturized equipment, any slight swing or angle deviation will have a negative impact on the air pressure control and air intake efficiency in the piston chamber 7.

[0077] When the hinge parts become loose due to wear, the amplitude of the swing may increase further, which may cause the air intake path to be blocked or leak, thereby affecting the equipment's inflation efficiency and performance.

[0078] The present application adopts a design in which the piston rod 1 and the piston disc 2 are integrally formed, eliminating the complexity of the hinged parts, so that the piston disc 2 and the piston rod 1 become a whole. This design eliminates the problems of joint wear and fatigue, and the overall structure is more stable and reliable. In high-speed reciprocating motion, the integrally formed structure can maintain high precision and stability, thereby extending the service life of the equipment.

[0079] At the same time, since there are no movable joints, the one-piece design occupies less space in the miniaturized air pump 8, which helps to make the device compact.

[0080] In addition, the one-piece design maintains the relative stability of the piston disc 2 and the inner wall of the piston chamber 7, avoiding the poor sealing problem caused by angle deviation and swing in the hinged design. In the one-piece structure, the movement trajectory of the piston disc 2 is more consistent, which can ensure that the air pressure and air intake path in the piston chamber 7 are stable during the compression and return process, thereby improving the performance of the device.

[0081] On the basis of the above, radial freedom is provided by adding L3 band to improve adaptability. Specifically, in the one-piece design, although the piston disc 2 and the piston rod 1 are fixed as a whole, during high-speed reciprocating motion, the piston disc 2 may be affected by the slight friction force or external stress of the inner wall of the piston cavity 7, thereby generating a certain radial displacement. By setting L3 in the annular groove 3, sufficient radial freedom is provided for the piston ring 4.

[0082] This degree of freedom enables the piston ring 4 to adjust when the piston disc 2 is slightly displaced, thereby better adapting to changes in the piston chamber 7. The setting of L3 ensures that the piston ring 4 can maintain the openness of the intake path within the range of radial freedom. When the piston disc 2 is slightly displaced during high-speed movement, the piston ring 4 can adjust its position to ensure that the air flow groove 5 can always remain unobstructed. This design avoids the intake blockage caused by the displacement of the piston disc 2, thereby improving the intake efficiency of the miniaturized air pump 8.

[0083] By providing radial freedom for the piston ring 4, the L3 design enables the piston disc 2 to more flexibly adapt to environmental changes in the piston chamber 7 during movement, thereby reducing wear problems caused by rigid fixation. Compared with the articulated form, which is prone to wear due to joint fatigue, the one-piece molding plus the L3 design greatly reduces the friction between the piston ring 4 and the inner wall of the piston chamber 7, improving the durability of the equipment. At the same time, this radial freedom not only ensures the long-term and efficient operation of the equipment, but also extends the overall service life of the air pump 8.

[0084] On the other hand, the value range of L3 is 0 to X mm, the purpose of which is to ensure that the piston ring 4 has a certain amount of movement to ensure sealing, while preventing excessive movement from causing a decrease in compression performance.

[0085] When L3 = 0mm, the piston ring 4 is completely fixed without any room for movement. This design can theoretically ensure that the piston ring 4 is always in a fixed position, but in actual work, complete fixation may not be able to effectively cope with temperature changes, pressure fluctuations or subtle changes caused by piston movement, which can easily lead to seal failure or increased wear.

[0086] When L3 = Xmm, the piston ring 4 has a degree of freedom in the annular groove 3 equal to its axial dimension X, which allows the piston ring 4 to move fully to adapt to various changes. However, excessive movement may cause the piston ring 4 to become unstable during operation, thereby affecting the compression performance, causing gas leakage or unstable gas flow during the compression process.

[0087] Therefore, the piston ring 4 needs a certain amount of movement to adapt to changes in pressure, temperature and other factors during the working process. For example, the gas may produce a certain vibration or displacement during the compression process, and the piston ring 4 must be able to freely adjust its position in the annular groove 3 to ensure that it is always in close contact with the inner wall of the piston cylinder to maintain sealing. In actual work, the materials of the piston ring 4 and the annular groove 3 will expand or contract slightly with changes in temperature and pressure. Therefore, setting an appropriate amount of movement can ensure that the piston ring 4 can maintain a good sealing effect under various working conditions.

[0088] In summary, the value range of L3 is set to 0 to Xmm in order to ensure that the piston ring 4 has a certain amount of movement while ensuring that it does not move excessively and affect the compression performance. Through appropriate movement space, the piston ring 4 can freely adjust its position during operation to maintain a good sealing effect and prevent gas leakage and compression efficiency reduction caused by excessive movement.

[0089] In a specific embodiment, in the radial direction of the piston rod 1, the cross-sectional area of ​​the annular groove 3 is S2, and the total projected area of ​​the airflow groove 5 on the same cross-section is S1; Moreover, 0.05≤S1 / S2≤0.3.

[0090] like Figures 4 to 9 , Fig.13 As shown, for example, the airflow slot 5 is rectangular, and the airflow slot 5 has a length M1 and a width M2, and the number of the airflow slots 5 is Xq. Among them, the projection area of ​​the air flow groove 5 on the same cross section is S1=M1*M2*Xq; Wherein, the cross-sectional area of ​​the annular groove 3 is S2=Π*L2^2 / 4; Moreover, 0.05≤S1 / S2≤0.3.

[0091] The ratio of S1 to S2 describes the proportion of the airflow groove 5 relative to the annular groove 3, which has an important influence on the air flow and compression efficiency during the compression process. By controlling this ratio, the compression ratio and the inflation speed can be adjusted. Specifically: The smaller the S1 / S2 ratio (closer to 0.05): it means that there are fewer or smaller gas flow slots. This can achieve a higher compression ratio, and the pump is faster and more efficient when compressing high-pressure gas. However, in this case, the gas flow channel is narrower, the air flow resistance increases, and greater energy consumption may be required.

[0092] The larger the S1 / S2 ratio (closer to 0.3), the larger the airflow channel. This design is suitable for low-pressure work because the larger channel can reduce airflow resistance and increase gas flow speed. However, the larger total area of ​​the airflow slot 5 will lead to a decrease in compression ratio, which will reduce efficiency and slow down compression speed when high pressure is applied.

[0093] Therefore, when S1 / S2 is close to 0.05, the proportion of airflow slot 5 is small and the compression ratio is relatively high. This design is suitable for scenarios that require high-pressure output, such as in high-pressure air pumps, where the pressure of the gas can be quickly increased. The disadvantage is that the airflow resistance increases and more energy may be required to drive. When S1 / S2 is close to 0.3, the proportion of airflow slot 5 is large and the compression ratio decreases. This design is suitable for low-pressure and fast inflation scenarios, where the gas can flow at a faster speed, but when high-pressure gas needs to be compressed, the efficiency will decrease and the inflation speed will slow down.

[0094] By controlling the ratio of S1 / S2 between 0.05 and 0.3, a balance can be achieved between the compression ratio and the gas flow rate. A smaller ratio is suitable for the compression requirements of high-pressure gas, which can improve the compression efficiency and the pumping speed; a larger ratio is more suitable for the rapid pumping operation of low-pressure gas, but the compression ratio is relatively low, and the speed of forming high pressure during pumping is slow. The total area of ​​the airflow slot 5 can be adjusted according to different work requirements to achieve the best compression effect and pumping efficiency.

[0095] In a specific embodiment, the cross section of the piston ring 4 is circular and is made of elastic material.

[0096] In the traditional leather cup structure, the leather cup is prone to wear, fatigue and deformation under high frequency and high pressure environment. With the increase of the number of uses, the elasticity and sealing performance of the leather cup gradually decreases, resulting in a decrease in the pumping efficiency.

[0097] Specifically, when the cup-type air pump 8 works to 100 times (inflation times) and a specific pressure (100 psi), the wear of the cup will significantly affect its sealing effect, causing the air pump 8 to take longer to reach the set pressure. In this case, the decay time is extended to 30 seconds to 40 seconds, which indicates that the life of the cup is limited and the decay speed is fast.

[0098] The piston ring 4 in this embodiment adopts a circular cross-section and elastic material, and under the same working conditions (100 times of inflation, 100 psi pressure), the decay time is maintained at about 10 seconds. This means that under the same working conditions, the design of the present application can more effectively maintain the performance of the air pump 8 and significantly extend the life of the equipment.

[0099] Compared with the existing leather cup form, the design of the present application can maintain more stable sealing performance and lower wear rate in high-frequency and high-pressure working environments, thereby avoiding a rapid increase in decay time. This performance advantage enables the air pump 8 to complete its tasks more efficiently in long-term use.

[0100] It should be noted that the attenuation time refers to the increasing trend of the time required for the air pump 8 to reach the set pressure, and is an important indicator for evaluating the life and efficiency of the air pump 8.

[0101] Moreover, when the piston reciprocates, the contact surface of the circular cross section with the inner wall of the piston cavity 7 is evenly distributed in a curve, which can effectively reduce friction and wear rate, thereby extending the service life of the piston ring 4. Miniaturized air pumps 8 usually work at a higher frequency, so reducing wear is crucial to maintaining long-term stable operation of the equipment.

[0102] In addition, the round cross-section design can avoid concentrated wear on corners and protrusions, which is especially critical in miniaturized designs because the tolerances of spaces and components are small and concentrated wear may cause serious performance problems.

[0103] In a specific embodiment, the axis A of the piston rod 1 is not coaxial with the center point P of the piston plate 2 .

[0104] In the prior art, the axis of the piston rod 1 is usually coaxial with the center point of the piston disc 2. Although this design can ensure the linear reciprocating motion of the piston, it also has some obvious defects: Due to the coaxial design, the leather cup remains symmetrical and fully expanded during the piston return and compression process. Although this tight fit helps the sealing, it also greatly increases the resistance to the piston movement and forms a large damping. The leather cup will experience radial expansion and contraction in each movement. This continuous physical deformation not only increases wear, but also increases the resistance of intake and exhaust, making the motor consume more power when pushing the piston.

[0105] In a miniaturized air pump 8, the motor power is usually limited, and high damping will cause the motor to be overloaded during startup and operation, resulting in increased energy consumption and shortened equipment life.

[0106] In the present application, the axis A of the piston rod 1 and the center point P of the piston disc 2 are designed to be non-coaxial to enhance the motion characteristics of the piston disc 2 and the overall performance of the device: By making the axis of the piston rod 1 non-coaxial with the center point of the piston plate 2, the piston plate 2 can generate a slightly offset motion trajectory during reciprocating motion. This offset helps to expose more air flow groove 5 area during the return stroke, thereby optimizing the intake path and increasing the intake volume.

[0107] Due to the non-coaxial motion track of the piston disc 2, the contact point and contact angle between the piston ring 4 and the inner wall of the piston chamber 7 can be optimized during the return and compression process, so that it can reduce unnecessary friction while maintaining the seal. This design is particularly suitable for miniaturized equipment to achieve better sealing effect and higher work efficiency in a limited space.

[0108] In a specific embodiment, the piston rod 1 has a connecting end B1 and a connecting end B2; Wherein, the connecting end B1 is connected to the piston disc 2; Wherein, the connection end B2 is used to connect with the driving member 802; The value range of the length L4 from the connection end B1 to the connection end B2 can be selected according to actual needs.

[0109] like Figures 10 to 12 As shown, the second embodiment of the present invention provides an air pump 8, comprising: A piston rod as described in the above embodiment.

[0110] The air pump 8 provided in this embodiment has all the beneficial effects mentioned above, which will not be described in detail here.

[0111] In a specific embodiment, the air pump 8 includes a shell 801 , and the shell 801 has a height ranging from 65 mm to 70 mm, a length ranging from 40 mm to 50 mm, and a width ranging from 25 mm to 30 mm.

[0112] In a specific embodiment, the driving member 802 is a brushless motor, and is eccentrically connected to the connecting end B2 of the piston rod 1 through an eccentric wheel mechanism 803. The brushless motor is arranged along the length direction of the housing 801, and the length ranges from 20 mm to 25 mm, and the remaining space of the housing 801 in the length direction is used to assemble the eccentric wheel mechanism 803. In the height direction of the housing 801, the height range of the brushless motor is 20 mm to 25 mm.

[0113] In a specific embodiment, a battery 804 is installed above the driving member 802. In the height direction of the housing 801, the height of the battery 804 ranges from 35mm to 38mm, and the length ranges from 15mm to 18mm. On one side of the battery 804, the piston rod 1 and the piston cylinder are installed, and the height of the entire structure ranges from 35mm to 38mm, and the length ranges from 20mm to 25mm.

[0114] Generally speaking, the inner space of the housing 801 is divided into four areas: the battery 804 is installed in the upper left area, the piston rod 1 and the piston cylinder are installed in the upper right area, the brushless motor is installed in the lower left area, and the eccentric wheel mechanism 803 is installed in the lower right area.

[0115] In a specific embodiment, a display screen is included and is located on one of the walls of the housing 801 .

[0116] In a specific implementation, it includes an air pressure detection module, which is arranged at the air outlet of the air pump 8.

[0117] 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.

[0118] 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 piston rod, characterized in that: include: Piston rod and piston disc; The piston rod and the piston disc are integrally formed; Wherein, the circumferential wall surface of the piston disc forms an annular groove; A piston ring is sleeved on the annular groove and has a clearance fit with the annular groove; Wherein, along the axial direction of the piston rod, the axial dimension of the annular groove is H1, and the axial dimension of the piston ring is X; H1-X=C1, the value range of C1 is 0.2mm-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.

2. The piston rod according to claim 1, 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 piston 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 piston cylinder is D4; Among them, L2≥D4; D4>D2>D1.

3. The piston rod according to claim 2, 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.

4. The piston rod according to claim 1, characterized in that: The inner diameter D4 of the piston cylinder ranges from 10 mm to 45 mm.

5. The piston rod according to claim 1, characterized in that: The distance between the inner ring surface of the piston ring and the bottom of the annular groove is L3; Moreover, the value range of L3 is 0mm to Xmm.

6. The piston rod according to claim 1, characterized in that: In the radial direction of the piston rod, the cross-sectional area of ​​the annular groove is S2, and the total projected area of ​​the airflow groove on the same cross-sectional area is S1; Moreover, 0.05≤S1 / S2≤0.

3.

7. The piston rod according to any one of claims 1 to 6, characterized in that The cross section of the piston ring is circular and is made of elastic material.

8. The piston rod according to any one of claims 1 to 6, characterized in that The axis A of the piston rod is not coaxial with the center point P of the piston disc.

9. The piston rod according to any one of claims 1 to 6, characterized in that The piston rod has a connecting end B1 and a connecting end B2; Wherein, the connecting end B1 is connected to the piston disc; Wherein, the connection end B2 is used to connect with the driving member.

10. An air pump, characterized in that: include: A piston rod as claimed in any one of claims 1 to 9 above.

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