Piston disc structure, piston assembly and inflating pump

Abstract

The invention discloses a piston disc structure, a piston assembly and an inflating pump, and relates to the technical field of inflating devices. According to the main technical scheme, the piston comprises a piston disc and a piston ring, an air inlet is formed in one end of the piston disc, and a mounting groove is formed in the side wall of the piston disc; the piston ring sleeves the piston disc and is slidably arranged in the mounting groove, and the side, away from the groove bottom of the mounting groove, of the piston ring is used for being attached to the inner wall of the piston cylinder. A first gap is reserved between the piston ring and the groove bottom of the mounting groove, a containing groove is formed in the end, close to the air inlet, of the piston ring, and a first abutting part is formed between the groove wall, away from the first gap, of the containing groove and the side wall, away from the first gap, of the piston ring. In the compression process, the first abutting part inclines towards the inner wall of the piston cylinder under extrusion of gas in the containing groove. The risk that the sealing performance of the piston ring is reduced due to abrasion is reduced, the acting force between the first abutting part and the inner wall of the piston barrel is increased, the sealing performance between the piston ring and the piston barrel is improved, and the inflating efficiency is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of air pumping devices, and in particular to a piston disc structure, a piston assembly and an air pump. Background Art

[0002] In portable applications, 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 providing users with a lighter and more convenient experience, and improving the flexibility of use and market competitiveness of the equipment.

[0003] In the existing air pump, during the high-speed reciprocating motion of the piston ring in the piston cylinder, the friction between the piston ring and the inner wall of the piston cylinder will cause severe wear of the piston ring, thereby resulting in low sealing between the piston ring and the piston cylinder during the compression process. Summary of the invention

[0004] The purpose of the present invention is to provide a piston disc structure, a piston assembly and an air pump, which solves the problem that during the high-speed reciprocating motion of the piston ring of the existing air pump in the piston cylinder, the friction between the piston ring and the inner wall of the piston cylinder will cause severe wear of the piston ring, thereby resulting in low sealing between the piston ring and the piston cylinder during the compression process.

[0005] In order to solve the above technical problems, the present invention adopts the following technical solutions:

[0006] A piston disc structure comprises a piston disc and a piston ring, wherein an air inlet hole is provided on an end surface of one end of the piston disc, and a mounting groove is provided on a side wall of the piston disc, wherein the mounting groove is communicated with the air inlet hole; the piston ring is sleeved on the piston disc, and the piston ring is slidably arranged in the mounting groove, and a side of the piston ring away from the bottom of the mounting groove is used to fit against an inner wall of a piston cylinder; a first gap is reserved between the piston ring and the bottom of the mounting groove, a receiving groove is provided on an end of the piston ring close to the air inlet hole, and a first abutting portion is formed between a groove wall of the receiving groove away from the first gap and a side wall of the piston ring away from the first gap ; When the piston disc is in an air intake state, one end of the piston ring close to the air inlet hole is in contact with the groove wall of the mounting groove close to the air inlet hole, a second gap is formed between the one end of the piston ring away from the air inlet hole and the groove wall of the mounting groove away from the air inlet hole, a third gap is formed between the side wall of the other end of the piston disc and the piston cylinder, and an air intake channel is formed between the first gap, the second gap, the third gap and the air inlet hole; when the piston disc is in a compression state, one end of the piston ring away from the air inlet hole is in contact with the groove wall of the mounting groove away from the air inlet hole, and the force between the first abutting portion and the inner wall of the piston cylinder increases.

[0007] A further technical solution is: a support portion is provided at the bottom of the accommodating groove; the support portion extends along one end of the piston disc toward the other end of the piston disc; the support portion is penetrated in the piston ring; a plurality of support portions are provided, and the plurality of support portions are axially arranged around the piston disc; the first gap is formed between the side where two adjacent support portions are close to each other, and the bottom of the accommodating groove and the piston ring; wherein a second abutting portion is formed between the groove wall of the accommodating groove close to the first gap and the side wall of the piston ring close to the first gap, and when the piston disc is in a compressed state, the second abutting portion abuts against the support portion.

[0008] A further technical solution is that: a width D of the first abutting portion is greater than a width d of the second abutting portion.

[0009] A further technical solution is: when the piston disc is in an air suction state, the first abutting portion and the second abutting portion are both in contact with the groove wall of the mounting groove close to the air inlet hole.

[0010] A further technical solution is: a first fitting surface is provided at one end of the piston ring away from the air inlet hole; a second fitting surface is provided at a groove wall of the mounting groove away from the air inlet hole; and the first fitting surface fits the second fitting surface.

[0011] In a second aspect, a piston assembly is provided, comprising the piston disc structure as described in the first aspect, wherein the piston assembly further comprises a connecting rod connected to the other end of the piston disc.

[0012] In the third aspect, an air pump is provided, comprising a piston assembly as described in the second aspect, the air pump further comprising a piston cylinder, a slide groove being provided at one end of the piston cylinder, and an air passage being provided at the bottom of the slide groove; wherein the piston disc and the connecting rod are both arranged in the slide groove, and the piston disc and the connecting rod are arranged in sequence along the direction from the bottom of the slide groove to the groove mouth of the slide groove.

[0013] A further technical solution is: the diameter of the slide groove is denoted as L; wherein 10mm≤L≤45mm.

[0014] A further technical solution is: the distance between the axis of the connecting rod and the axis of the sliding groove is recorded as M; wherein 0mm≤M≤6mm.

[0015] A further technical solution is: the depth of the slide groove is recorded as N, and the length of the connecting rod is recorded as n; wherein, 14mm≤N≤21mm, and 22.3mm≤n≤31.7mm.

[0016] Compared with the prior art, the present invention has the following beneficial effects:

[0017] When the piston ring reciprocates at high speed in the piston cylinder, the piston ring is close to the inner wall of the piston cylinder, and wear occurs due to the friction between the piston ring and the piston cylinder. During the compression process, the first abutting portion is squeezed by the gas in the accommodating groove and tilts toward the inner wall of the piston cylinder. It is expected to reduce the risk of reduced sealing performance of the piston ring due to wear, increase the force between the first abutting portion and the inner wall of the piston cylinder, improve the sealing performance between the piston ring and the piston cylinder, and improve the inflation efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 This is a schematic structural diagram of a piston disc structure in this embodiment;

[0019] Figure 2 It is a schematic diagram of the top view of the piston disc structure when a piston ring of the piston disc structure in this embodiment is attached to the groove wall of the installation groove away from the air inlet hole;

[0020] Figure 3 for Figure 2 Schematic diagram of the cross-sectional structure at AA in the middle;

[0021] Figure 4 It is a schematic diagram of the top view of the piston disc structure when a piston ring of the piston disc structure in this embodiment is attached to the groove wall of the installation groove close to the air inlet hole;

[0022] Figure 5 for Figure 4 Schematic diagram of the cross-sectional structure at the middle BB;

[0023] Figure 6 is a schematic cross-sectional structural diagram of a piston disc used in a piston disc structure in this embodiment;

[0024] Figure 7 It is a front structural schematic diagram of a piston disc structure when a piston ring of a piston disc structure in this embodiment is attached to a groove wall of the mounting groove away from the air inlet hole;

[0025] Figure 8 for Figure 7 Schematic diagram of the cross-sectional structure at CC in the middle;

[0026] Fig. 9 is a structural schematic diagram of a piston assembly in this embodiment;

[0027] Fig.10 This is a schematic diagram of the structure of an air pump in this embodiment;

[0028] Fig.11 This is a schematic diagram of a top view of an air pump in this embodiment;

[0029] Fig.12 for Fig.11Schematic diagram of the cross-sectional structure at DD in the middle.

[0030] Marks and corresponding parts names in the attached drawings:

[0031] 1-piston disc; 2-air inlet hole; 3-installation groove; 4-piston ring; 5-first gap; 6-accommodating groove; 7-first abutting portion; 8-second gap; 9-third gap; 10-support portion; 11-second abutting portion; 12-first fitting surface; 13-second fitting surface; 14-connecting rod; 15-piston cylinder; 16-slide groove; 17-air duct. DETAILED DESCRIPTION

[0032] The present invention will be further described below in conjunction with the accompanying drawings.

[0033] Example 1

[0034] This embodiment provides a piston disc structure, such as Figure 1-Figure 8 As shown, it comprises a piston disc 1 and a piston ring 4, an end surface of one end of the piston disc 1 is provided with an air inlet hole 2, a side wall of the piston disc 1 is provided with a mounting groove 3, and the mounting groove 3 is communicated with the air inlet hole 2; the piston ring 4 is sleeved on the piston disc 1, the piston ring 4 is slidably arranged in the mounting groove 3, and the side of the piston ring 4 away from the bottom of the mounting groove 3 is used to fit the inner wall of the piston cylinder 15; a first gap 5 is reserved between the piston ring 4 and the bottom of the mounting groove 3, an accommodating groove 6 is provided at one end of the piston ring 4 close to the air inlet hole 2, and a first abutting portion 7 is formed between the groove wall of the accommodating groove 6 away from the first gap 5 and the side wall of the piston ring 4 away from the first gap 5; when When the piston disc 1 is in an intake state, one end of the piston ring 4 close to the air inlet hole 2 fits against the groove wall of the mounting groove 3 close to the air inlet hole 2, and a second gap 8 is formed between the end of the piston ring 4 away from the air inlet hole 2 and the groove wall of the mounting groove 3 away from the air inlet hole 2, a third gap 9 is formed between the side wall of the other end of the piston disc 1 and the piston cylinder 15, and an air inlet channel is formed between the first gap 5, the second gap 8, the third gap 9 and the air inlet hole 2; when the piston disc 1 is in a compression state, one end of the piston ring 4 away from the air inlet hole 2 fits against the groove wall of the mounting groove 3 away from the air inlet hole 2, and the force between the first abutting portion 7 and the inner wall of the piston cylinder 15 increases.

[0035] Exemplarily, in the implementation process, the side wall of the piston disc 1 is provided with a mounting groove 3, and the mounting groove 3 is an annular structure that allows the piston disc 1 to be axially arranged. An air inlet 2 is opened on the end surface of one end of the piston disc 1, and the air inlet 2 extends from one end of the piston disc 1 to the other end of the piston disc 1 until the air inlet 2 is connected with the mounting groove 3. The diameter of the other end of the piston disc 1 is smaller than the inner diameter of the piston cylinder 15, so that the side wall of the other end of the piston disc 1 can form a third gap 9 with the inner wall of the piston cylinder 15.

[0036] The piston ring 4 can be made of materials such as polytetrafluoroethylene, reinforced polyamide (nylon reinforced material) with good wear resistance, appropriate elasticity, and the ability to maintain good sealing performance under high pressure. The piston ring 4 is sleeved on the piston disc 1, and the piston ring 4 is slidably located in the installation groove 3. The piston ring 4 fits on the groove bottom of the installation groove 3, or a certain gap is reserved between the piston ring 4 and the groove bottom of the installation groove 3, so that the piston ring 4 can slide back and forth in the installation groove 3 along one end of the piston disc 1 toward the other end of the piston disc 1 under the action of external force. The side of the piston ring 4 away from the groove bottom of the installation groove 3 is used to fit with the inner wall of the piston cylinder 15. A first gap 5 is reserved between the piston ring 4 and the groove bottom of the installation groove 3, and a receiving groove 6 is opened at one end of the piston ring 4 close to the air inlet 2, and a first abutment portion 7 is formed between the groove wall of the receiving groove 6 away from the first gap 5 and the side wall of the piston ring 4 away from the first gap 5.

[0037] When in use, the piston disc structure is installed in the piston cylinder 15, and the side of the piston ring 4 away from the bottom of the installation groove 3 is attached to the inner wall of the piston cylinder 15. At this time, a third gap 9 is formed between the side wall of the other end of the piston disc 1 (the end of the piston disc 1 without the air inlet 2) and the inner wall of the piston cylinder 15.

[0038] During the air intake process, when the piston disc 1 initially moves along one end of the piston cylinder 15 toward the other end of the piston cylinder 15 under the action of external force, the piston ring 4 moves in the mounting groove 3 along the other end of the piston disc 1 (the end of the piston disc 1 without the air inlet hole 2) toward one end of the piston disc 1 (the end of the piston disc 1 with the air inlet hole 2) under the action of the friction force between the piston ring 4 and the piston cylinder 15 until the piston ring 4 fits on the groove wall of the mounting groove 3 close to the air inlet hole 2 (the groove wall of the mounting groove 3 close to the end of the piston disc 1), and a second gap 8 is formed between the end of the piston ring 4 away from the air inlet hole 2 and the groove wall of the mounting groove 3 away from the air inlet hole 2 (the groove wall of the mounting groove 3 close to the other end of the piston disc 1), as shown in FIG. Figure 5As shown. At this time, an air intake channel is formed between the third gap 9, the second gap 8, the first gap 5 and the air intake hole 2. As the piston disc 1 moves further along one end of the piston cylinder 15 toward the other end of the piston cylinder 15 under the action of external force, the piston ring 4 moves synchronously with the piston disc 1 under the limiting action of the groove wall of the mounting groove 3, and allows the gas to enter the interior of the piston cylinder 15 through the third gap 9, the second gap 8, the first gap 5 and the air intake hole 2 in sequence. Thereby achieving the purpose of air intake. At the same time, the existence of the accommodating groove 6 reserves space for the first abutting portion 7 to tilt along the piston cylinder 15 toward the piston disc 1. It is expected to reduce the friction between the piston ring 4 and the inner wall of the piston cylinder 15, thereby reducing the wear rate of the piston ring 4 and extending the service life of the piston ring 4.

[0039] During the compression process, when the piston disc 1 initially moves from the other end of the piston cylinder 15 to one end of the piston cylinder 15 under the action of external force, the piston ring 4 moves in the mounting groove 3 along one end of the piston disc 1 (the end of the piston disc 1 with the air inlet hole 2) to the other end of the piston disc 1 (the end of the piston disc 1 without the air inlet hole 2) under the action of the friction force between the piston ring 4 and the piston cylinder 15 until the piston ring 4 fits on the groove wall of the mounting groove 3 away from the air inlet hole 2 (the groove wall of the end of the mounting groove 3 away from the piston disc 1), and a gap is formed between the end of the piston ring 4 close to the air inlet hole 2 and the groove wall of the mounting groove 3 close to the air inlet hole 2 (the groove wall of the other end of the mounting groove 3 away from the piston disc 1), as shown in FIG. Figure 3 As shown. As the piston disc 1 moves further from the other end of the piston cylinder 15 to one end of the piston cylinder 15 under the action of external force, part of the gas in the piston cylinder 15 enters the receiving groove 6 through the gap between the end of the piston ring 4 close to the air inlet 2 and the groove wall of the installation groove 3 close to the air inlet 2. At this time, the first abutting portion 7 tends to tilt toward the inner wall of the piston cylinder 15 under the pressure of the gas in the receiving groove 6. It is expected to increase the pressure between the first abutting portion 7 and the inner wall of the piston cylinder 15, thereby enhancing the sealing effect during the compression process.

[0040] When the piston ring 4 reciprocates at high speed in the piston cylinder 15, the piston ring 4 is close to the inner wall of the piston cylinder 15, and wear occurs under the friction between the piston ring 4 and the piston cylinder 15. During the compression process, the first abutting portion 7 is squeezed by the gas in the accommodating groove 6 and tilts toward the inner wall of the piston cylinder 15. It is expected to reduce the risk of the piston ring 4 and the sealing performance being reduced due to wear, and increase the force between the first abutting portion 7 and the inner wall of the piston cylinder 15, so as to improve the sealing performance between the piston ring 4 and the piston cylinder 15 and improve the inflation efficiency.

[0041] In this embodiment, if Figure 8As shown, a support portion 10 is provided at the bottom of the accommodating groove 6; the support portion 10 extends along one end of the piston disc 1 in the direction of the other end of the piston disc 1; the support portion 10 is penetrated in the piston ring 4; the number of the support portions 10 is provided in a plurality, and the plurality of support portions 10 are axially arranged around the piston disc 1; the first gap 5 is formed between the side where two adjacent support portions 10 are close to each other, and the bottom of the accommodating groove 6 and the piston ring 4; wherein a second abutting portion 11 is formed between the groove wall of the accommodating groove 6 close to the first gap 5 and the side wall of the piston ring 4 close to the first gap 5, and when the piston disc 1 is in a compressed state, the second abutting portion 11 abuts against the support portion 10.

[0042] Exemplarily, in the implementation process, the bottom of the accommodating groove 6 is provided with a support portion 10 by welding, screwing or integral molding, and the support portion 10 is a strip structure extending from one end of the piston disc 1 to the other end of the piston disc 1. There are multiple support portions 10, and the multiple support portions 10 are evenly distributed around the axis of the piston disc 1 and are spaced apart. The piston ring 4 is sleeved on the support portion 10 to form a first gap 5 between the side where the adjacent support portions 10 are close to each other, the bottom of the accommodating groove 6, and the piston ring 4. It is expected to achieve the purpose of allowing the piston ring 4 to slide freely under the guidance of the support portion 10. At the same time, it is expected to achieve the purpose of reducing the contact area between the piston ring 4 and the piston disc 1 during the sliding process, thereby reducing the wear rate of the piston disc 1.

[0043] A second abutting portion 11 is formed between a groove wall of the accommodating groove 6 close to the first gap 5 and a side wall of the piston ring 4 close to the first gap 5 . During the compression state, the second abutting portion 11 abuts against the supporting portion 10 .

[0044] When in use, during the compression process, when the piston disc 1 initially moves from the other end of the piston cylinder 15 to one end of the piston cylinder 15 under the action of external force, the piston ring 4 moves in the mounting groove 3 along one end of the piston disc 1 (the end of the piston disc 1 with the air inlet 2) to the other end of the piston disc 1 (the end of the piston disc 1 without the air inlet 2) under the action of the friction between the piston ring 4 and the piston cylinder 15, until the piston ring 4 fits on the groove wall of the mounting groove 3 away from the air inlet 2 (the groove wall of the mounting groove 3 away from the end of the piston disc 1), and a gap is formed between the end of the piston ring 4 close to the air inlet 2 and the groove wall of the mounting groove 3 close to the air inlet 2 (the groove wall of the mounting groove 3 away from the other end of the piston disc 1). As the piston disc 1 further moves from the other end of the piston cylinder 15 to one end of the piston cylinder 15 under the action of external force, part of the gas in the piston cylinder 15 enters the containing groove 6 through the gap between the end of the piston ring 4 close to the air inlet 2 and the groove wall of the mounting groove 3 close to the air inlet 2. At this time, the first abutting portion 7 tends to tilt toward the inner wall of the piston cylinder 15 under the pressure of the gas in the receiving groove 6. It is expected to increase the pressure between the first abutting portion 7 and the inner wall of the piston cylinder 15, thereby enhancing the sealing effect during the compression process. At the same time, the second abutting portion 11 tends to tilt toward the support portion 10 under the pressure of the gas in the receiving groove 6, and fits with the support portion 10. It is expected to increase the interaction force between the second abutting portion 11 and the support portion 10 during the compression process, thereby increasing the sealing effect between the second abutting portion 11 and the support portion 10, reducing the risk of gas leakage through the gap between the piston ring 4 and the support portion 10, and improving the inflation efficiency.

[0045] In actual use, the installation space between the piston disc 1 and the piston cylinder 15 is limited, and the wear rate between the first abutting portion 7 and the piston cylinder 15 is faster than the wear rate between the second abutting portion 11 and the piston disc 1. When the first abutting portion 7 is severely worn, the sealing performance of the piston ring 4 will be reduced. Therefore, in order to extend the service life of the piston ring 4. In this embodiment, Figure 5 As shown, the width D of the first abutting portion 7 is greater than the width d of the second abutting portion 11 .

[0046] For example, in the implementation process, the width of the first abutting portion 7 is recorded as D, and the width of the second abutting portion 11 is recorded as d. Wherein, D>d. By setting a wider first abutting portion 7, it is expected to achieve the purpose of extending the wear time of the first abutting portion 7 and thus extending the service life of the piston ring 4.

[0047] In this embodiment, if Figure 5 As shown, when the piston disc 1 is in the air suction state, the first abutting portion 7 and the second abutting portion 11 are both in contact with the groove wall of the mounting groove 3 close to the air inlet 2 .

[0048] Exemplarily, during the implementation, during the air intake process, when the piston disc 1 initially moves along one end of the piston cylinder 15 toward the other end of the piston cylinder 15 under the action of external force, the piston ring 4 moves in the mounting groove 3 along the other end of the piston disc 1 (the end of the piston disc 1 where the air inlet hole 2 is not set) toward one end of the piston disc 1 (the end of the piston disc 1 where the air inlet hole 2 is set) under the action of the friction force between the piston ring 4 and the piston cylinder 15 until the piston ring 4 is attached to the groove wall of the mounting groove 3 near the air inlet hole 2 (the groove wall of the mounting groove 3 near the end of the piston disc 1), that is, the first abutment portion 7 and the second abutment portion 11 are both attached to the groove wall of the mounting groove 3 near the air inlet hole 2.

[0049] It is expected that during the air intake process, the interaction force between the first abutting portion 7 and the groove wall of the mounting groove 3, as well as the interaction force between the second abutting portion 11 and the groove wall of the mounting groove 3, will be increased, thereby increasing the sealing performance between the first abutting portion 7 and the groove wall of the mounting groove 3, as well as the second abutting portion 11 and the groove wall of the mounting groove 3 (i.e. increasing the sealing performance of the groove opening of the accommodating groove 6), thereby reducing the risk of gas entering the accommodating groove 6, thereby reducing the risk of gas entering the accommodating groove 6, resulting in an increase in the interaction force between the first abutting portion 7 and the piston cylinder 15, as well as the interaction force between the second abutting portion 11 and the support member, so as to reduce the friction between the piston ring 4 and the piston cylinder 15, as well as the piston disk 1, reduce the wear rate of the piston ring 4, and extend the service life of the piston ring 4.

[0050] In the prior art, the longitudinal cross-sectional area of ​​the piston ring 4 is circular. During the compression process, the piston ring 4 and the groove wall of the installation groove 3 are in line contact and sealing. When the piston ring 4 is worn, the sealing performance between the piston ring 4 and the groove wall of the installation groove 3 is reduced, and the risk of gas leakage in the piston cylinder 15 through the piston ring 4 and the groove wall of the installation groove 3 is relatively large. Therefore, in order to reduce the risk of gas leakage in the piston cylinder 15 through the piston ring 4 and the groove wall of the installation groove 3 during the compression process. In this embodiment, as shown in FIG. Figure 3 As shown, the piston ring 4 is provided with a first fitting surface 12 at one end away from the air inlet hole 2 ; the groove wall of the mounting groove 3 away from the air inlet hole 2 is provided with a second fitting surface 13 ; the first fitting surface 12 is fitted to the second fitting surface 13 .

[0051] Exemplarily, during implementation, a first fitting surface 12 is provided at one end of the piston ring 4 away from the air inlet hole 2. The first fitting surface 12 may be a region with a certain width on the end surface of the piston ring 4 away from the air inlet hole 2, or may refer to a region with a certain width dimension on the end of the piston ring 4 away from the air inlet hole 2. The first fitting surface 12 may be a curved surface, an inclined surface, a flat surface, etc. A second fitting surface 13 is provided on the groove wall of the mounting groove 3 away from the air inlet hole 2. The second fitting surface 13 may be a region with a certain width on the groove wall of the mounting groove 3 away from the air inlet hole 2. And the second fitting surface 13 is adapted to the first fitting surface 12 in shape and size. In other words, the first fitting surface 12 and the second fitting surface 13 can fit tightly.

[0052] During the compression process, when the piston disc 1 moves initially from the other end of the piston cylinder 15 to one end of the piston cylinder 15 under the action of external force, the piston ring 4 moves in the installation groove 3 along one end of the piston disc 1 (the end of the piston disc 1 with the air inlet 2) to the other end of the piston disc 1 (the end of the piston disc 1 without the air inlet 2) under the action of the friction between the piston ring 4 and the piston cylinder 15, until the piston ring 4 fits on the groove wall of the installation groove 3 away from the air inlet 2 (the groove wall of the end of the installation groove 3 away from the piston disc 1), that is, the first fitting surface 12 fits on the second fitting surface 13. It is expected that when the piston ring 4 is slightly worn, the piston ring 4 can still maintain a high sealing performance with the groove wall of the installation groove 3, thereby reducing the risk of gas leakage in the piston cylinder 15 through the groove wall between the piston ring 4 and the groove wall of the installation groove 3.

[0053] Example 2

[0054] This embodiment provides a piston assembly, such as Fig. 9 As shown, it includes the piston disc structure as described in Example 1, and the piston assembly also includes a connecting rod 14, and the connecting rod 14 is connected to the other end of the piston disc 1.

[0055] For example, in the implementation process, the connecting rod 14 is connected to the other end of the piston disc 1 (i.e., the end of the piston disc 1 where the air inlet 2 is not provided) by means of screw connection, welding or integral molding, etc., so as to facilitate the transmission of the movement of the external power source (such as a crankshaft or a motor) to the piston disc 1 through the connecting rod 14, so that the piston disc 1 can reciprocate in the piston cylinder 15.

[0056] Example 3

[0057] This embodiment provides an air pump, such as Figure 10-12As shown, it includes the piston assembly as described in Example 2, and the air pump also includes a piston cylinder 15, one end of the piston cylinder 15 is provided with a slide groove 16, and the bottom of the slide groove 16 is provided with an air channel 17; wherein, the piston disc 1 and the connecting rod 14 are both arranged in the slide groove 16, and the piston disc 1 and the connecting rod 14 are arranged in sequence along the bottom of the slide groove 16 toward the notch of the slide groove 16.

[0058] Exemplarily, in the implementation process, a slide groove 16 is provided at one end of the piston cylinder 15, and the piston disc 1 and the connecting rod 14 are both inserted into the slide groove 16, and the piston disc 1 and the connecting rod 14 are arranged in sequence along the direction from the bottom of the slide groove 16 to the notch of the slide groove 16. The slide groove 16 provides a movement space for the reciprocating movement of the piston disc 1 and the connecting rod 14 to ensure that the piston disc 1 and the connecting rod 14 can reciprocate smoothly in the piston cylinder 15. An air channel 17 is provided at the bottom of the slide groove 16, and the air channel 17 is used to discharge the gas in the piston cylinder 15 out of the piston cylinder 15 during the compression process.

[0059] The piston ring 4 on the piston plate 1 fits against the inner wall of the piston cylinder 15 (the groove wall of the slide groove 16). It is expected that during the compression process, part of the gas in the piston cylinder 15 enters the receiving groove 6 through the gap between the end of the piston ring 4 close to the air inlet 2 and the groove wall of the installation groove 3 close to the air inlet 2, so that the first abutting portion 7 tends to tilt toward the inner wall of the piston cylinder 15 under the pressure of the gas in the receiving groove 6. It is expected that the pressure between the first abutting portion 7 and the inner wall of the piston cylinder 15 can be increased, thereby enhancing the sealing effect during the use of the air pump and improving the air pumping efficiency.

[0060] In this embodiment, if Fig.12 As shown, the diameter of the slide groove 16 is recorded as L, wherein 10mm≤L≤45mm; the distance between the axis of the connecting rod 14 and the axis of the slide groove 16 is recorded as M, wherein 0mm≤M≤6mm.

[0061] Exemplarily, in the implementation process, the diameter of the slide groove 16 is recorded as L, and 10mm≤L≤45mm. It is expected to ensure that the slide groove 16 can provide enough space for the piston plate 1 and the connecting rod 14 to reciprocate smoothly while maintaining the compactness of the structure. The distance between the axis of the connecting rod 14 and the axis of the slide groove 16 is recorded as M, and 0mm≤M≤6mm. It is expected to ensure that the connecting rod 14 can run smoothly in the slide groove 16 and reduce unnecessary mechanical stress, thereby improving the overall reliability and durability of the air pump.

[0062] In this embodiment, if Fig.12 As shown, the depth of the slide groove 16 is recorded as N, and the length of the connecting rod 14 is recorded as n; wherein, 14 mm≤N≤21 mm, and 22.3 mm≤n≤31.7 mm.

[0063] For example, in the implementation process, the depth of the slide groove 16 is recorded as N, 14 mm ≤ N ≤ 21 mm, in order to ensure that the piston plate 1 and the connecting rod 14 have sufficient movement space while maintaining the compactness of the structure.

[0064] The length of the connecting rod 14 is recorded as n, and 22.3 mm ≤ n ≤ 31.7 mm, in order to reduce unnecessary mechanical stress of the connecting rod 14 and thus improve the reliability and durability of the equipment.

[0065] Although the present invention is described herein with reference to a number of illustrative embodiments of the present invention, it will be appreciated that those skilled in the art may devise many other modifications and implementations that fall within the scope and spirit of the principles disclosed herein. More specifically, within the scope of the present disclosure, drawings, and claims, a variety of variations and improvements may be made to the components and / or layout of the subject combination layout. In addition to variations and improvements made to the components and / or layout, other uses will also be apparent to those skilled in the art.

Claims

1. A piston disc structure, characterized in that: include: A piston disc (1), wherein an air inlet hole (2) is provided on an end surface of one end of the piston disc (1), and a mounting groove (3) is provided on a side wall of the piston disc (1), wherein the mounting groove (3) is in communication with the air inlet hole (2); A piston ring (4), wherein the piston ring (4) is sleeved on the piston plate (1), the piston ring (4) is slidably arranged in the mounting groove (3), and the side of the piston ring (4) away from the bottom of the mounting groove (3) is used to fit the inner wall of the piston cylinder (15); a first gap (5) is reserved between the piston ring (4) and the bottom of the mounting groove (3), a receiving groove (6) is provided at one end of the piston ring (4) close to the air inlet (2), and a first abutting portion (7) is formed between the groove wall of the receiving groove (6) away from the first gap (5) and the side wall of the piston ring (4) away from the first gap (5); When the piston disc (1) is in an air intake state, one end of the piston ring (4) close to the air inlet hole (2) is attached to the groove wall of the mounting groove (3) close to the air inlet hole (2), a second gap (8) is formed between one end of the piston ring (4) away from the air inlet hole (2) and the groove wall of the mounting groove (3) away from the air inlet hole (2), a third gap (9) is formed between the side wall of the other end of the piston disc (1) and the piston cylinder (15), and an air intake channel is formed between the first gap (5), the second gap (8), the third gap (9) and the air inlet hole (2); When the piston disc (1) is in a compressed state, the end of the piston ring (4) away from the air inlet hole (2) is in contact with the groove wall of the mounting groove (3) away from the air inlet hole (2), and the force between the first abutting portion (7) and the inner wall of the piston cylinder (15) increases.

2. The piston disc structure according to claim 1, characterized in that: The bottom of the accommodating groove (6) is provided with a supporting portion (10); The support portion (10) extends along one end of the piston disc (1) in a direction toward the other end of the piston disc (1); The support portion (10) is inserted into the piston ring (4); The number of the support parts (10) is set to be multiple, and the multiple support parts (10) are arranged axially around the piston disc (1); The first gap (5) is formed between the side where two adjacent support portions (10) are close to each other, the bottom of the accommodating groove (6), and the piston ring (4); A second abutting portion (11) is formed between the groove wall of the accommodating groove (6) close to the first gap (5) and the side wall of the piston ring (4) close to the first gap (5), and when the piston disc (1) is in a compressed state, the second abutting portion (11) abuts against the supporting portion (10).

3. The piston disc structure according to claim 2, characterized in that: The width D of the first abutting portion (7) is greater than the width d of the second abutting portion (11).

4. The piston disc structure according to claim 3, characterized in that: When the piston disc (1) is in an air intake state, the first abutment portion (7) and the second abutment portion (11) are both in contact with the groove wall of the installation groove (3) close to the air inlet hole (2).

5. The piston disc structure according to claim 1, characterized in that: A first fitting surface (12) is provided at one end of the piston ring (4) away from the air inlet hole (2); A second fitting surface (13) is provided on a groove wall of the installation groove (3) away from the air inlet hole (2); The first bonding surface (12) is bonded to the second bonding surface (13).

6. A piston assembly, characterized in that: The piston assembly comprises a piston disc structure as claimed in any one of claims 1 to 5, and further comprises: A connecting rod (14), wherein the connecting rod (14) is connected to the other end of the piston disc (1).

7. An air pump, characterized in that: The piston assembly as claimed in claim 6, wherein the air pump further comprises: A piston cylinder (15), wherein a slide groove (16) is provided at one end of the piston cylinder (15), and an air passage (17) is provided at the bottom of the slide groove (16); The piston disc (1) and the connecting rod (14) are both arranged in the slide groove (16), and the piston disc (1) and the connecting rod (14) are arranged in sequence along the direction from the bottom of the slide groove (16) to the notch of the slide groove (16).

8. The air pump according to claim 7, characterized in that: The diameter of the slide groove (16) is denoted as L; Among them, 10mm≤L≤45mm.

9. The air pump according to claim 8, characterized in that: The distance between the axis of the connecting rod (14) and the axis of the sliding groove (16) is denoted as M; wherein 0mm≤M≤6mm.

10. The air pump according to claim 7, characterized in that: The depth of the slide groove (16) is recorded as N, and the length of the connecting rod (14) is recorded as n; wherein, 14 mm≤N≤21 mm, and 22.3 mm≤n≤31.7 mm.

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