High compression damping solenoid valve shock absorber with hydraulic buffer

Abstract

The application relates to a high-compression-damping electromagnetic valve shock absorber with hydraulic buffering and belongs to the technical field of electromagnetic valve shock absorbers. The application comprises a piston rod, a guider, a working cylinder, an intermediate cylinder, an oil storage cylinder, a piston, an electromagnetic valve and a bottom valve, the guider and the bottom valve are respectively arranged at two ends in the oil storage cylinder, the working cylinder is arranged between the guider and the bottom valve, the intermediate cylinder is arranged between the working cylinder and the oil storage cylinder, the piston rod penetrates through the guider and extends to the working cylinder, the piston is arranged at one end of the piston rod in the working cylinder, the electromagnetic valve is arranged between the intermediate cylinder and the oil storage cylinder, first and second one-way valves are respectively arranged on the side wall of the working cylinder close to the guider and the bottom valve, and the first and second one-way valves are both one-way valves flowing from the working cylinder to the intermediate cylinder. The application can effectively increase the compression damping force of the shock absorber, simultaneously provide the recovery hydraulic buffering effect and meet the damping requirement.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of electromagnetic valve shock absorber, and particularly relates to a high compression damping electromagnetic valve shock absorber with hydraulic buffer. BACKGROUND

[0002] The shock absorber is one of important components of the vehicle chassis suspension, and plays a decisive role in the operability and comfort of the vehicle. The operability and comfort have different requirements for the damping force of the shock absorber. The damping force of the traditional shock absorber is fixed, and cannot meet the demand of the best operability and the best comfort at the same time. The electromagnetic valve shock absorber has an intermediate cylinder and an electromagnetic valve more than the ordinary shock absorber, and the working cylinder wall surface is provided with a small hole, so that the oil in the working cylinder and the intermediate cylinder is communicated with each other. In the recovery and compression stroke, part of the oil in the working cylinder enters the intermediate cylinder through the small hole on the working cylinder, and then flows into the oil storage cylinder after throttling by the electromagnetic valve, so that the size of the damping force can be adjusted by changing the throttling area of the electromagnetic valve.

[0003] The common electromagnetic valve shock absorber structure, such as the electronically controlled shock absorber disclosed in the Chinese utility model patent with the patent number ZL202020131911.9, is provided with a small hole on the upper cavity of the working cylinder, and the oil flows into the intermediate cylinder from the small hole of the upper cavity of the working cylinder in the recovery and compression stroke of the shock absorber, and then flows into the electromagnetic valve for throttling effect. In the recovery stroke, part of the liquid flows into the lower cavity from the upper cavity of the working cylinder, and a pressure difference is generated by the throttling effect of the recovery valve; another part of the liquid flows into the intermediate cylinder from the upper cavity of the working cylinder, and a pressure difference is generated after throttling by the electromagnetic valve; and the total flow of the liquid is large, the flow through the electromagnetic valve and the recovery valve is also large, and the generated pressure difference is large, so that a large recovery damping force is obtained. However, in the compression stroke, part of the liquid first flows into the upper cavity from the lower cavity of the working cylinder, and then flows into the electromagnetic valve through the intermediate cylinder, in order to avoid the phenomenon of idle stroke, it is necessary to ensure that the flow to the electromagnetic valve is sufficient, so the throttling effect of the flow through valve between the upper and lower cavities of the working cylinder must be low enough, so the pressure difference between the upper and lower cavities of the working cylinder is very small; another part of the liquid flows into the oil storage cylinder from the lower cavity of the working cylinder, and a pressure difference is generated by the throttling of the compression valve; and the total flow of the liquid is small, the flow through the electromagnetic valve and the compression valve is also small, and the generated pressure difference is small, so only a very low compression damping force can be obtained. At present, the electromagnetic valve shock absorber generally adopts a large-diameter piston rod structure to increase the total flow in the compression stroke, so as to improve the compression damping force. However, due to the limitation of the size of the working cylinder, the diameter of the piston rod cannot be increased indefinitely, and the increase of the diameter of the piston rod will also reduce the recovery damping force, so the effect of improving the compression damping force by this method is very limited. SUMMARY

[0004] The present application aims at solving the problems of the prior art, and provides a high compression damping electromagnetic valve shock absorber with hydraulic buffering, which can effectively increase the compression damping force of the shock absorber, provide recovery hydraulic buffering effect, and meet the damping requirement.

[0005] The present application is achieved by the following technical scheme.

[0006] The high compression damping electromagnetic valve shock absorber with hydraulic buffering comprises a piston rod, a guide, a working cylinder, an intermediate cylinder, an oil storage cylinder, a piston, an electromagnetic valve and a bottom valve, the guide and the bottom valve are respectively arranged at two ends in the oil storage cylinder, the working cylinder is arranged between the guide and the bottom valve, the intermediate cylinder is arranged between the working cylinder and the oil storage cylinder, the piston rod passes through the guide and extends into the working cylinder, the piston is arranged at one end of the piston rod in the working cylinder, the electromagnetic valve is arranged between the intermediate cylinder and the oil storage cylinder, first and second one-way valves are respectively arranged on the side wall of the working cylinder close to the guide and the bottom valve, and the first and second one-way valves are both one-way valves flowing from the working cylinder to the intermediate cylinder.

[0007] As a preferred embodiment of the present application, when the piston rod is in the maximum stretching state, the first one-way valve is arranged between the piston and the bottom valve.

[0008] As a preferred embodiment of the present application, the first and second one-way valves each comprise a valve piece groove arranged on the outer wall of the working cylinder, a valve hole arranged at the bottom of the valve piece groove, and a valve piece connected to one end of the bottom of the valve piece groove.

[0009] As a preferred embodiment of the present application, the bottom of the valve piece groove is smooth and flat.

[0010] As a preferred embodiment of the present application, a sealing plug is arranged between the end of the working cylinder and the end of the intermediate cylinder, and a first sealing ring is arranged between the sealing plug and the outer side wall of the working cylinder and the inner side wall of the intermediate cylinder.

[0011] As a preferred embodiment of the present application, the sealing plug is provided with a limiting boss matched with the end of the intermediate cylinder, and an axial adjustment gap is arranged between the limiting boss and the end of the intermediate cylinder.

[0012] As a preferred embodiment of the present application, the size of the axial adjustment gap is 0.5-3 mm.

[0013] As a preferred embodiment of the present application, an oil nozzle seat is arranged on the outer side wall of the intermediate cylinder, a second sealing ring is arranged on the end face of the oil nozzle seat, the electromagnetic valve is tightly attached to the end face of the oil nozzle seat, and a fixing ring is connected between the oil nozzle seat and the outer side wall of the electromagnetic valve.

[0014] As a preferred embodiment of the present application, a wear-resistant layer is arranged on the surface of the piston in contact with the working cylinder.

[0015] As the invention is preferred, the piston is provided with a recovery valve and a flow valve, and the bottom valve is provided with a compression valve and a compensation valve.

[0016] The advantages of the present invention are:

[0017] 1. During compression stroke, the liquid directly enters the intermediate chamber from the lower chamber of the working cylinder through the second one-way valve and then flows to the electromagnetic valve. The liquid does not need to flow from the lower chamber of the working cylinder to the upper chamber and then enter the intermediate chamber. Therefore, a flow valve with large throttling effect can be used to generate a large pressure difference between the upper and lower chambers of the working cylinder, thereby greatly improving the compression damping force and synchronously improving the compression damping adjustment range, solving the problem of too low compression damping force in the prior art.

[0018] 2. When the piston recovery stroke passes through the upper first one-way valve of the working cylinder, both the upper and lower one-way valves are closed, the one-way valve flow is rapidly reduced, the flow to the electromagnetic valve is reduced to zero, and the shock absorber recovery damping force will rapidly increase to play a hydraulic buffer role. The size of the hydraulic buffer stroke depends on the distance between the upper first one-way valve of the working cylinder and the distance between the guide, which is easy to adjust.

[0019] 3. By setting an axial adjustment gap between the intermediate cylinder and the sealing plug, the machining precision error is compensated, the oil nozzle seat and the center line of the electromagnetic valve are kept coincident, the sealing performance is improved, the leakage is reduced, and the stability of the damping force value is improved.

[0020] 4. The oil nozzle seat end face and the electromagnetic valve are sealed by a plane, which is simpler to install than a circumferential seal, the sealing ring is uniformly stressed without eccentric force, leakage is reduced, and the stability of the damping force value is improved. BRIEF DESCRIPTION OF DRAWINGS

[0021] Figure 1 A cross-sectional view of a high compression damping electromagnetic valve shock absorber with hydraulic buffer is provided for the present embodiment;

[0022] Figure 2 A working cylinder structure schematic diagram is provided for the present embodiment;

[0023] Figure 3 A cross-sectional view of the internal structure of a high compression damping electromagnetic valve shock absorber with hydraulic buffer is provided for the present embodiment;

[0024] Figure 4 A Figure 3 An enlarged structure schematic diagram of point B;

[0025] Figure 5 A schematic diagram of the oil flow during recovery stroke of a high compression damping electromagnetic valve shock absorber with hydraulic buffer is provided for the present embodiment;

[0026] Figure 6An oil flow direction diagram of a high compression damping electromagnetic valve shock absorber compression stroke with hydraulic buffer provided by the embodiment;

[0027] In the figure: 1-piston rod; 2-guide; 3-working cylinder; 31-first check valve; 32-second check valve; 311-valve piece slot; 312-valve hole; 313-valve piece; 4-intermediate cylinder; 42-sealing plug; 43-first sealing ring; 45-second sealing ring; 46-nozzle seat; 47-fixed ring; 48-sealing intermediate cavity; 5-oil storage cylinder; 6-piston; 61-recovery valve; 62-flow-through valve; 7-electromagnetic valve; 8-bottom valve; 81-compression valve; 82-compensation valve; 9-working cylinder upper cavity; 10-working cylinder lower cavity. DETAILED DESCRIPTION

[0028] The application will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0029] As Figure 1 and 3As shown, the embodiment provides a high compression damping electromagnetic valve shock absorber with hydraulic buffer, comprising: a piston rod 1, a guide 2, a working cylinder 3, an intermediate cylinder 4, an oil storage cylinder 5, a piston 6, an electromagnetic valve 7 and a bottom valve 8. Wherein, the guide 2 and the bottom valve 8 are respectively arranged at both ends of the oil storage cylinder 5, and the guide 2 is at the upper end and the bottom valve 8 is at the lower end. The two ends of the working cylinder 3 are respectively sealed and connected to the guide 2 and the bottom valve 8, and the intermediate cylinder 4 is gap-set outside the working cylinder 3, and the gap between them constitutes a sealed intermediate cavity 48. The intermediate cylinder 4 is provided with a sealing plug 42 at both ends, the inner circumferential surface of the sealing plug 42 is in close contact with the outer circumferential surface of the working cylinder 3, the outer circumferential surface of the sealing plug 42 is in close contact with the inner circumferential surface of the intermediate cylinder 4, and at the same time, one end of the sealing plug is in contact with the guide 2 or the bottom valve 8 and is axially positioned, the outer circumferential surface of the sealing plug is provided with a boss matched with the end of the intermediate cylinder 4, and in order to ensure the sealing between the working cylinder 3 and the intermediate cylinder 4, the inner circumferential surface and the outer circumferential surface of the sealing plug 42 are both provided with a first sealing ring 43. One end of the piston rod 1 passes through the end of the oil storage cylinder 5 and the guide 2 in turn and extends into the working cylinder 3, and the end of the piston rod 1 extending into the working cylinder 3 is provided with the piston 6, which moves up and down along the inner wall of the working cylinder 3 under the stretching and compression action of the piston rod 1. The outer edge of the piston 6 is in contact with the inner edge of the working cylinder to form a moving pair, and the contact surface forms a dynamic seal for oil, which divides the working cylinder 3 into an upper working cylinder 9 and a lower working cylinder 10. An oil nozzle seat 46 is welded on the circumferential surface of the intermediate cylinder 4, the end surface of the oil nozzle seat 46 is in close contact with the oil inlet end surface of the electromagnetic valve 7, and is sealed by a second sealing ring 45 on the end surface, and the two are fixed by a fixed ring 47. The above-mentioned flat sealing mode makes the sealing ring bear force more evenly without eccentric force, which can effectively reduce leakage and improve damping force value stability. The oil outlet of the electromagnetic valve 7 is connected with the oil storage cylinder 5 and is also sealed and connected with the side wall of the oil storage cylinder 5. In addition, as shown in Figure 4 and 5 The piston 6 is provided with a recovery valve 61 and a flow-through valve 62, the recovery valve allows oil to flow from the upper working cylinder 9 to the lower working cylinder 10, and the flow-through valve 62 allows oil to flow from the lower working cylinder 10 to the upper working cylinder 9. The bottom valve 8 is provided with a compression valve 81 and a compensation valve 82, the compression valve 81 allows oil to flow from the lower working cylinder 10 to the oil storage cylinder 5, and the compensation valve 82 allows oil to flow from the oil storage cylinder 5 to the lower working cylinder 10.

[0030] As shown in Figure 2 and 3 The upper part and the lower part of the outer side wall of the working cylinder 3 are respectively provided with a first one-way valve 31 and a second one-way valve 32, and the two one-way valves only allow oil to flow from the working cylinder 3 to the intermediate cylinder 4, and when the piston rod 1 is in the maximum stretching state, the first one-way valve 31 is in the lower working cylinder 10. The working principle of the shock absorber is as follows:

[0031] like Figure 5 As shown, during the recovery stroke, the upper chamber 9 of the working cylinder is compressed. A portion of the oil in the upper chamber 9 flows from the first one-way valve 31 into the intermediate cylinder 4, and then flows into the oil reservoir 5 after being throttled by the solenoid valve 7. The other portion of the oil flows into the lower chamber of the working cylinder from the recovery valve 61 inside the piston 6. That is, the pressure difference is generated by the throttling effect of the solenoid valve 7 and the recovery valve 61 on the oil, thereby obtaining the recovery damping force. At the same time, the lower chamber 10 of the working cylinder is stretched, the second one-way valve 32 is closed, and compensation oil is required. In addition to receiving the oil from the upper chamber 9 of the working cylinder, it is also necessary to receive the oil from the oil reservoir through the compensation valve 82 inside the bottom valve 8.

[0032] During the upward recovery motion of piston 6, from completely covering the first check valve 31 to completely passing through it, until reaching the ultimate recovery position, the first check valve 31 closes. The oil in the upper chamber 9 of the working cylinder cannot flow into the intermediate cylinder through the first check valve 31, and the flow rate of the solenoid valve 7 also decreases to zero. The oil in the upper chamber 9 of the working cylinder can only flow into the lower chamber 10 of the working cylinder through the recovery valve 61 inside the piston. Therefore, the recovery damping force of the shock absorber increases rapidly during this process, acting as a hydraulic buffer at the end of the entire recovery stroke to improve the stability of the shock absorber. Furthermore, the timing of the activation of this hydraulic buffering effect can be adjusted by changing the position of the first check valve 31 on the working cylinder 3. For example, increasing the distance between the first check valve 31 and the upper end of the working cylinder will cause piston 6 to pass through the first check valve 31 earlier during the recovery process, thus entering the aforementioned hydraulic buffering action earlier.

[0033] like Figure 6 As shown, during the compression stroke, the lower chamber 10 of the working cylinder is compressed. A portion of the oil in the lower chamber 10 flows into the intermediate cylinder 4 through the lower check valve 32, and then flows into the oil reservoir 5 after being throttled by the solenoid valve 7. Another portion of the oil flows into the upper chamber 9 of the working cylinder through the flow valve 62 in the piston 6. The remaining portion of the oil flows into the oil reservoir 5 through the compression valve 81 in the bottom valve 8. That is, the compression damping force is provided by the throttling effect of the solenoid valve 7, the flow valve 62, and the compression valve 81 on the oil. Since the oil does not need to flow from the lower chamber 10 of the working cylinder into the upper chamber and then into the intermediate chamber 4, but can flow directly from the lower chamber 10 of the working cylinder into the intermediate chamber 4 through the second check valve 32, it is ensured that the flow to the solenoid valve 7 is sufficient and there is no idle stroke. Therefore, we can use the flow valve 62 with a large throttling effect, so that a large pressure difference can be generated between the upper and lower chambers of the working cylinder, thereby greatly improving the compression damping force. At the same time, it also increases the selection range of the throttling performance of the flow valve 62, that is, it improves the adjustment range of the compression damping force. During this process, the upper chamber 9 of the working cylinder is stretched, the first one-way valve 31 is closed, and the upper chamber of the working cylinder can only receive oil from the lower chamber 10 of the working cylinder through the flow valve 62.

[0034] When the piston 6 starts compression from the limit position, the first one-way valve 31 and the second one-way valve 32 are both in the lower cavity 10 of the working cylinder, so the oil can flow into the intermediate cylinder 4 from the first one-way valve 31 and the second one-way valve 32 when the lower cavity 10 of the working cylinder is compressed, and the compression damping force is relatively small. When the piston 6 moves downward to completely cover the first one-way valve 31, the oil in the lower cavity 10 of the working cylinder cannot flow into the intermediate cylinder 4 from the first one-way valve 31, and the compression damping force is relatively large. Thus, the compression damping force is slightly increased at the beginning of the compression stroke, thereby improving the comfort of damping.

[0035] Specifically, as shown in Figure 2 The first one-way valve 31 and the second one-way valve 32 have the same structure, which includes a valve piece groove 311 arranged on the outer wall of the working cylinder, a valve hole 312 arranged on the bottom surface of the valve piece groove 311, and a valve piece 313 tightly combined with the rectangular groove 311 and completely covering the valve hole 312. The valve piece 313 is connected and fixed with the bottom surface of the valve piece groove 311 by a screw 314. The valve piece groove 311 is a smooth and flat rectangular groove to ensure the tightness of the valve piece 313 and the valve piece groove 311, avoid oil leakage, and make the valve piece 313 flat to ensure smooth opening.

[0036] In order to ensure the matching precision of the oil nozzle seat 46 and the electromagnetic valve 7, that is, the center lines of the two coincide, thereby improving the sealing performance, reducing oil leakage, and improving the stability of the damping force value. As shown in Figure 4 An axial adjustment gap t is arranged between the boss of the sealing plug 42 and the end of the intermediate cylinder 4, so that the intermediate cylinder 4 can move axially within the range of t to compensate for the machining precision error. The axial adjustment gap refers to the sum of the gaps between the intermediate cylinder 4 and the bosses of the two sealing plugs 42. t is generally 0.5-3mm, preferably 1.5mm.

[0037] In addition, since the working cylinder 3 has two one-way valve holes 312 on the inner wall, and the powder metallurgy piston 6 is easily worn when passing through the valve hole 312, a wear-resistant layer is arranged on the surface of the piston 6 in contact with the working cylinder. The wear-resistant layer can be made of SF-1 material with PTFE inner layer.

[0038] The above is only a preferred specific embodiment of the present application, which is one implementation based on the overall concept of the present application, and the protection scope of the present application is not limited thereto. Any changes or replacements within the technical scope disclosed by the present application can be easily thought by those skilled in the art, which should be covered within the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.

Claims

1. A high-compression damping solenoid valve vibration damper with hydraulic buffer, comprising a piston rod, a guide, a working cylinder, an intermediate cylinder, an oil reservoir, a piston, a solenoid valve, and a bottom valve, wherein the guide and the bottom valve are respectively disposed at both ends of the oil reservoir, the working cylinder is disposed between the guide and the bottom valve, the intermediate cylinder is disposed between the working cylinder and the oil reservoir, the piston rod extends through the guide into the working cylinder, the piston is disposed at the end of the piston rod located within the working cylinder, and the solenoid valve is disposed between the intermediate cylinder and the oil reservoir, characterized in that... The working cylinder sidewall is provided with a first check valve and a second check valve near the guide and bottom valve, respectively. Both the first check valve and the second check valve are check valves that flow from the working cylinder to the intermediate cylinder. When the piston rod is in the maximum tension state, the first check valve is located between the piston and the bottom valve.

2. The high-compression damping solenoid valve vibration damper with hydraulic buffer according to claim 1, characterized in that, Both the first check valve and the second check valve include a valve plate groove on the outer wall of the working cylinder, a valve hole at the bottom of the valve plate groove, and a valve plate connected at one end to the bottom of the valve plate groove.

3. A high-compression damping solenoid valve vibration damper with hydraulic buffer according to claim 2, characterized in that, The bottom of the valve plate groove is smooth and flat.

4. A high-compression damping solenoid valve vibration damper with hydraulic buffer according to claim 1, characterized in that, A sealing plug is provided between the ends of the working cylinder and the intermediate cylinder, and a first sealing ring is provided between the sealing plug and the outer wall of the working cylinder and the inner wall of the intermediate cylinder.

5. A high-compression damping solenoid valve vibration damper with hydraulic buffer according to claim 4, characterized in that, The sealing plug is provided with a limiting boss that matches the end of the intermediate cylinder, and an axial adjustment gap is provided between the limiting boss and the end of the intermediate cylinder.

6. A high-compression damping solenoid valve vibration damper with hydraulic buffer according to claim 5, characterized in that, The axial adjustment gap is 0.5-3mm.

7. A high-compression damping solenoid valve vibration damper with hydraulic buffer according to claim 1, characterized in that, The outer wall of the intermediate cylinder is provided with an oil nozzle seat, the end face of the oil nozzle seat is provided with a second sealing ring, the solenoid valve is in close contact with the end face of the oil nozzle seat, and a fixing ring is connected between the oil nozzle seat and the solenoid valve.

8. A high-compression damping solenoid valve vibration damper with hydraulic buffer according to claim 1, characterized in that, The piston has a wear-resistant layer on the surface that contacts the working cylinder.

9. A high-compression damping solenoid valve vibration damper with hydraulic buffer according to claim 1, characterized in that, The piston is equipped with a recovery valve and a flow valve, and the bottom valve is equipped with a compression valve and a compensation valve.

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