Passive adjustable damping force shock absorber and automobile

Abstract

The present invention relates to the technical field of shock absorbers, and specifically provides a passive adjustable damping force shock absorber and a car, aiming to solve the problem that the overall structure of the existing shock absorber is very complicated in order to achieve damping changes. To this end, the shock absorber of the present invention includes a cylinder, a piston, a piston rod, a first flow regulating valve, a second flow regulating valve and a guide structure, the first flow regulating valve is rotatably arranged on the first valve structure, the second flow regulating valve is rotatably arranged on the second valve structure, and the guide structure is arranged to enable the first flow regulating valve to rotate relative to the first valve structure and the second flow regulating valve to rotate relative to the second valve structure during the compression stroke and the extension stroke of the shock absorber, thereby adjusting the damping force of the shock absorber itself. The present invention can realize the passive adjustment of the damping force under different strokes by adding a simple structure, reduce the complexity of the structural design, and ensure the stability of the compression and extension of the shock absorber.

Description

Technical Field

[0001] The invention relates to the technical field of shock absorbers, and in particular provides a passive adjustable damping force shock absorber and a car. Background Art

[0002] Shock absorbers are commonly used components to achieve vibration reduction functions and are widely used in various fields. For example, in automobiles, shock absorbers, as important components of the suspension system, can improve the driving smoothness and ride comfort of the automobile. For example, in the structure where the shock absorber is connected to the frame and the axle, when the frame and the axle make reciprocating relative motion, the piston of the shock absorber also reciprocates in the cylinder, and the oil in the shock absorber cylinder repeatedly flows from one inner cavity to another through some narrow pores. At this time, the friction between the pore wall and the oil and the friction between the liquid molecules can form a damping force on the vibration, so that the vibration energy of the body and frame is converted into heat energy, which is then absorbed by the oil and the shock absorber cylinder and then dissipated into the atmosphere.

[0003] Most existing shock absorbers are fixed damping force shock absorbers. Once the valve system of the shock absorber is selected, it is impossible to adjust the damping force under different strokes. For example, when the compression stroke and the extension (recovery / rebound) stroke are at the maximum stroke, if a high damping force is to be achieved, it is necessary to add additional HCS (Hydraulic Compression Stop) and HRS (Hydraulic rebound stop). However, adding HCS and HRS will add additional valve systems and sub-cylinders, and the overall structure is very complicated. Some shock absorbers use variable damping force shock absorbers that can actively adjust the damping force, but this type of shock absorber requires the addition of an additional electromagnetic control system, and the overall structure is also very complicated.

[0004] In view of this, the art needs a new passive adjustable damping force shock absorber and a car to solve the above problems. Summary of the invention

[0005] The present invention aims to solve the above technical problem, that is, to solve the problem that the overall structure of the existing shock absorber is very complicated in order to achieve damping change.

[0006] In a first aspect, the present invention provides a passive adjustable damping force shock absorber, the shock absorber comprising a cylinder, a piston movable in the cylinder, and a piston rod whose inner end is connected to the piston, the piston dividing an internal chamber of the cylinder into a first chamber and a second chamber, the piston comprising a first valve structure and a second valve structure communicating with each other, the first valve structure being formed with a plurality of first valve ports communicating with the first chamber, the second valve structure being formed with a plurality of second valve ports communicating with the second chamber;

[0007] The shock absorber also includes a first flow regulating valve, a second flow regulating valve and a guide structure, the first flow regulating valve is rotatably arranged on the first valve structure, the second flow regulating valve is rotatably arranged on the second valve structure, the first flow regulating valve is formed with a first opening corresponding to the first valve port, the second flow regulating valve is formed with a second opening corresponding to the second valve port, the guide structure is configured to enable the first flow regulating valve to rotate relative to the first valve structure during the compression stroke and the extension stroke of the shock absorber to change the relative position of the corresponding first opening and the first valve port, thereby changing the flow area between the first opening and the first chamber, and to enable the second flow regulating valve to rotate relative to the second valve structure to change the relative position of the corresponding second opening and the second valve port, thereby changing the flow area between the second valve port and the second chamber, thereby adjusting the damping force of the shock absorber itself.

[0008] In the preferred technical solution of the above-mentioned passive adjustable damping force shock absorber, the guide structure includes a first guide member arranged on the first flow regulating valve, a second guide member arranged on the second flow regulating valve, and a spiral guide groove formed on the inner wall of the cylinder, and the first guide member and the second guide member are both guided and cooperated with the spiral guide groove.

[0009] In the preferred technical solution of the above passive adjustable damping force shock absorber, the first guide member includes a first guide bead and a first spring connecting the first guide bead to the first flow regulating valve, and the first guide bead is slidably arranged in the spiral guide groove; and / or

[0010] The second guide member includes a second guide bead and a second spring connecting the second guide bead with the second flow regulating valve, and the second guide bead is slidably disposed in the spiral guide groove.

[0011] In the preferred technical solution of the above-mentioned passive adjustable damping force shock absorber, the guide structure includes a first guide member arranged on the first flow regulating valve, a second guide member arranged on the second flow regulating valve, and a first spiral guide groove and a second spiral guide groove formed on the inner wall of the cylinder, the first guide member is guided and matched with the first spiral guide groove, and the second guide member is guided and matched with the second spiral guide groove.

[0012] In the preferred technical solution of the above-mentioned passive adjustable damping force shock absorber, the first guide member includes a first guide bead and a first spring connecting the first guide bead to the first flow regulating valve, and the first guide bead is slidably arranged in the first spiral guide groove, and the second guide member includes a second guide bead and a second spring connecting the second guide bead to the second flow regulating valve, and the second guide bead is slidably arranged in the second spiral guide groove.

[0013] In the preferred technical solution of the above passive adjustable damping force shock absorber, the first flow regulating valve is sleeved on the first valve structure and is located between the cylinder and the first valve structure.

[0014] The second flow regulating valve sleeve is arranged on the second valve structure and is located between the cylinder and the second valve structure.

[0015] In the preferred technical solution of the above-mentioned passive adjustable damping force shock absorber, the shape of the first valve structure and the shape of the first flow regulating valve are both annular, the multiple first valve ports are arranged in a ring-shaped distribution on the first valve structure, and the multiple first openings are arranged in a ring-shaped distribution on the first flow regulating valve.

[0016] In the preferred technical solution of the above-mentioned passive adjustable damping force shock absorber, the shape of the second valve structure and the shape of the second flow regulating valve are both annular, the multiple second valve ports are arranged in a ring-shaped distribution on the second valve structure, and the multiple second openings are arranged in a ring-shaped distribution on the second flow regulating valve.

[0017] In the preferred technical solution of the above passive adjustable damping force shock absorber, the first valve structure and the second valve structure are connected through a valve plate group.

[0018] In a second aspect, the present invention further provides a vehicle, comprising the passive adjustable damping force shock absorber described above.

[0019] When the above technical solution is adopted, the present invention can design the shock absorber to be adjustable in damping force during the compression stroke and the extension stroke, and it is passive adjustment rather than active adjustment, thereby avoiding the addition of additional HCS and HRS, or adding electromagnetic control systems such as active adjustment, avoiding the addition of particularly complex structures to achieve the adjustment of damping force under different strokes, reducing the complexity of structural design, and whether in the compression stroke or the extension stroke, the relative opening of the first opening of the first flow regulating valve and the first valve port of the first valve structure and the relative opening of the second opening of the second flow regulating valve and the second valve port of the second valve structure are gradually changed, which can ensure the stability of compression and extension of the shock absorber, provide stable holding force, and effectively alleviate system vibration.

[0020] Furthermore, the guide structure adopts a combination of guide beads, springs and spiral guide grooves, which can not only realize the rotation of the flow control valve relative to the valve structure in the compression stroke and extension stroke of the shock absorber to achieve oil flow regulation, and then adjust the damping force under different strokes, but also realize the guide structure as a non-pure rigid guide combination through the connection of the spring, that is, the guide combination has a certain flexibility variable, thereby avoiding extreme wear of the guide structure after long-term use, affecting the service life of the shock absorber.

[0021] Furthermore, the first flow regulating valve and the second flow regulating valve are respectively matched with different spiral guide grooves, thereby realizing independent configuration of the first flow regulating valve and the second flow regulating valve in terms of guidance, improving design flexibility, and providing more design possibilities for the passive damping adjustment of the shock absorber.

[0022] Furthermore, when the automobile of the present invention adopts the above-mentioned shock absorber, the above-mentioned technical effects can be achieved, and the complexity of the overall design of the automobile can be reduced. The design size of the shock absorber will not take up too much space, which is beneficial to the layout of the automobile body structure. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] The preferred embodiments of the present invention are described below in conjunction with the accompanying drawings, in which:

[0024] Figure 1 It is a schematic diagram of the overall structure of the first embodiment of the passive adjustable damping force shock absorber of the present invention;

[0025] Figure 2 The structure of the passive adjustable damping force shock absorber of the present invention is shown in FIG. Figure 1 (remove the cylinder);

[0026] Figure 3 The structure of the passive adjustable damping force shock absorber of the present invention is shown in FIG. Figure 2 (remove the cylinder);

[0027] Figure 4 The passive adjustable damping force shock absorber of the present invention is a cross-section Figure 1 ;

[0028] Figure 5 The passive adjustable damping force shock absorber of the present invention is a cross-section Figure 2 (The direction of oil flow when the belt is in the stretching stroke);

[0029] Figure 6 It is a structural schematic diagram of a first guide member of a passive adjustable damping force shock absorber of the present invention;

[0030] Figure 7 It is a structural schematic diagram of a second guide member of the passive adjustable damping force shock absorber of the present invention;

[0031] Figure 8 1 is a schematic diagram of the overall structure of a second embodiment of the passive adjustable damping force shock absorber of the present invention;

[0032] Fig. 9 It is a structural schematic diagram of an embodiment of a valve plate group of a passive adjustable damping force shock absorber of the present invention;

[0033] Fig.10 It is a structural schematic diagram of another embodiment of a valve plate assembly of a passive adjustable damping force shock absorber of the present invention;

[0034] List of reference numerals:

[0035] 1. Cylinder; 11. First chamber; 12. Second chamber;

[0036] 2. Piston; 21. First valve structure; 21a. First valve port; 22. Second valve structure; 22a. Second valve port; 23. Valve plate group; 23a. Spiral channel; 23b. First one-way valve; 23c. Second one-way valve;

[0037] 3. Piston rod;

[0038] 4. First flow regulating valve; 4a. First opening;

[0039] 5. Second flow regulating valve; 5a. Second opening;

[0040] 6. Guide structure; 61. First guide member; 611. First guide bead; 612. First spring; 62. Second guide member; 621. Second guide bead; 622. Second spring; 63. Spiral guide groove; 63a. First spiral guide groove; 63b. Second spiral guide groove. DETAILED DESCRIPTION

[0041] The preferred embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood by those skilled in the art that these embodiments are only used to explain the technical principles of the present invention and are not intended to limit the scope of protection of the present invention. For example, the shock absorber of the present invention can be applied to automobiles, and can also be applied to production equipment (such as CNC machining centers, machine tools, etc.), and can also be applied to household appliances (such as washing machines, air conditioners, etc.). The adjustment of such application objects does not constitute a limitation of the present invention and should be limited within the scope of protection of the present invention.

[0042] Based on the problem pointed out in the background technology that the overall structure of the existing shock absorber is very complex in order to achieve damping changes, the present invention provides a passive adjustable damping force shock absorber, which aims to achieve the adjustment of the damping force under different strokes by adding a simple structure, reduce the complexity of the structural design, and ensure the stability of the shock absorber in compression and tension.

[0043] It should be noted that, in the description of the present invention, terms such as "upper", "lower", "inside" and "outside" indicating directions or positional relationships are based on the directions or positional relationships shown in the drawings. This is only for the convenience of description and does not indicate or imply that the device or component must have a specific orientation or must be constructed and operated in a specific orientation. Therefore, it cannot be understood as a limitation on the present invention.

[0044] In addition, it should be noted that in the description of the present invention, unless otherwise clearly specified and limited, the terms "disposed" and "connected" should be understood in a broad sense. For example, "connected" can be a detachable connection or an integral connection; it can be directly connected or indirectly connected through an intermediate component. For those skilled in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0045] like Figures 1 to 5 As shown, the passive adjustable damping force shock absorber of the present invention comprises a cylinder 1, a piston 2, a piston rod 3, a first flow regulating valve 4, a second flow regulating valve 5 and a guide structure 6. The piston 2 is slidably disposed in the cylinder 1 and can move in the cylinder 1. The inner end of the piston rod 3 is connected to the piston 2, and the outer end of the piston rod 3 extends out of the cylinder 1. The piston 2 divides the internal chamber of the cylinder 1 into a first chamber 11 and a second chamber 12. Specifically, the volume of the first chamber 11 and the volume of the second chamber 12 change with the position of the piston 2. Figure 4As shown, the following is an example in which the first chamber 11 is closer to the outer end of the piston rod 3 than the second chamber 12. When the shock absorber is in the compression stroke, the volume of the first chamber 11 gradually increases, and the volume of the second chamber 12 gradually decreases, that is, the oil flows from the second chamber 12 to the first chamber 11. When the shock absorber is in the maximum stroke of the compression stroke (that is, the axial dimension of the shock absorber reaches the minimum), the volume of the first chamber 11 reaches the maximum value, and the volume of the second chamber 12 reaches the minimum value. When the shock absorber is in the extension stroke, the volume of the first chamber 11 gradually decreases, and the volume of the second chamber 12 gradually increases, that is, the oil flows from the first chamber 11 to the second chamber 12. When the shock absorber is in the maximum stroke of the extension stroke (that is, the axial dimension of the shock absorber reaches the maximum), the volume of the first chamber 11 reaches the minimum value, and the volume of the second chamber 12 reaches the maximum value. Correspondingly, the maximum stroke of the compression stroke of the shock absorber corresponds to the minimum stroke of the extension stroke of the shock absorber, and the minimum stroke of the compression stroke of the shock absorber corresponds to the maximum stroke of the extension stroke of the shock absorber. The piston 2 includes a first valve structure 21 and a second valve structure 22 that are connected to each other. The first valve structure 21 is formed with a plurality of first valve ports 21a that are connected to the first chamber 11, and the second valve structure 22 is formed with a plurality of second valve ports 22a that are connected to the second chamber 12. Specifically, the first valve structure 21 and the second valve structure 22 can be connected directly or through a valve plate group 23. All the first valve ports 21a connect the first chamber 11 with the second valve structure 22, and all the second valve ports 22a connect the second chamber 12 with the first valve structure 21. More specifically, Figure 5 As shown, when the first valve structure 21 and the second valve structure 22 are connected through the valve plate group 23, the first chamber 11 and the second chamber 12 are connected in sequence through all the first valve ports 21a, the valve plate group 23 and all the second valve ports 22a.

[0046] In the above, continue to see Figures 1 to 5The first flow regulating valve 4 is rotatably arranged on the first valve structure 21, and the second flow regulating valve 5 is rotatably arranged on the second valve structure 22. The first flow regulating valve 4 is formed with a first opening 4a corresponding to the first valve port 21a, and the second flow regulating valve 5 is formed with a second opening 5a corresponding to the second valve port 22a. The guide structure 6 is configured to enable the first flow regulating valve 4 to rotate relative to the first valve structure 21 during the compression stroke and the extension stroke of the shock absorber to change the relative position of the corresponding first opening 4a and the first valve port 21a, thereby changing the flow area between the first opening 4a and the first chamber 11, and to enable the second flow regulating valve 5 to rotate relative to the second valve structure 22 to change the relative position of the corresponding second opening 5a and the second valve port 22a, thereby changing the flow area between the second valve port 22a and the second chamber 12, thereby adjusting the damping force of the shock absorber itself. Specifically, the guide structure 6 can realize both the rotation of the first flow regulating valve 4 and the rotation of the second flow regulating valve 5. First, take the rotation of the first flow regulating valve 4 relative to the first valve structure 21 as an example for explanation. When the first flow regulating valve 4 rotates relative to the first valve structure 21, the relative opening of each corresponding first opening 4a and the first valve port 21a gradually changes. When the first opening 4a is completely aligned with the first valve port 21a, the oil can pass through the first valve port 21a at the maximum flow rate, that is, the oil flow rate between the first valve structure 21 and the first chamber 11 reaches the maximum. When the first opening 4a is completely misaligned with the first valve port 21a, the oil cannot pass through the first valve port 21a. The valve port 21a, that is, the first valve structure 21 and the first chamber 11 are isolated from each other. Through such a setting, when the first opening 4a and the first valve port 21a move from complete alignment to complete misalignment, the oil flow between the first valve structure 21 and the first chamber 11 gradually decreases, thereby generating a gradually increasing damping force. When the first opening 4a and the first valve port 21a move from complete misalignment to complete alignment, the oil flow between the first valve structure 21 and the first chamber 11 gradually increases, thereby generating a gradually decreasing damping force.Taking the rotation of the second flow regulating valve 5 relative to the second valve structure 22 as an example, when the second flow regulating valve 5 rotates relative to the second valve structure 22, the relative opening of each corresponding second opening 5a and the second valve port 22a gradually changes. When the second opening 5a is completely aligned with the second valve port 22a, the oil can pass through the second valve port 22a at the maximum flow rate, that is, the oil flow rate between the second valve structure 22 and the second chamber 12 reaches the maximum. When the second opening 5a is completely misaligned with the second valve port 22a, the oil cannot pass through the second valve port 22a. The valve port 22a, that is, the second valve structure 22 and the second chamber 12 are isolated from each other. Through such a setting, when the second opening 5a and the second valve port 22a move from complete alignment to complete misalignment, the oil flow between the second valve structure 22 and the second chamber 12 gradually decreases, thereby generating a gradually increasing damping force. When the second opening 5a and the second valve port 22a move from complete misalignment to complete alignment, the oil flow between the second valve structure 22 and the second chamber 12 gradually increases, thereby generating a gradually decreasing damping force.

[0047] It should be noted that in the present invention, since the guide structure 6 of the shock absorber in the compression stroke and the extension stroke makes the first flow regulating valve 4 rotate relative to the first valve structure 21, and makes the second flow regulating valve 5 rotate relative to the second valve structure 22, and the oil needs to flow between the first chamber 11 and the second chamber 12, the oil must pass through the first valve port 21a with changing flow rate, and the second valve port 22a with changing flow rate. At this time, the relative opening of the first opening 4a and the first valve port 21a and the relative opening of the second opening 5a and the second valve port 22a follow the "minimum principle", that is, as long as one of the flow area opened by the first opening 4a and the flow area opened by the second opening 5a is decreasing, the overall oil flow rate will be reduced, thereby continuously increasing the damping force. Through such a design principle, different guide structures 6 can be designed to determine the relationship between different stroke positions of the shock absorber in the compression stroke and the extension stroke and the rotation angle of the first flow regulating valve 4, the rotation angle of the second flow regulating valve 5, the initial relative position and the final relative position between the first opening 4a and the first valve port 21a, and the initial relative position and the final relative position between the second opening 5a and the second valve port 22a, so as to realize passive adjustment of the damping force in different compression strokes and extension strokes, and the damping force size at each position point in the stroke can be flexibly designed according to actual needs. This will be further elaborated in combination with various design scenarios below.

[0048] For example, when the maximum stroke of the compression stroke and the maximum stroke of the extension stroke of the shock absorber both require high damping force, the guide structure 6 can be set to ensure that the corresponding first opening 4a and the first valve port 21a are fully aligned and the corresponding second opening 5a and the second valve port 22a are fully aligned when the piston 2 is in the middle section of the compression stroke (i.e., corresponding to the middle section of the extension stroke), so as to ensure that the oil passes through the first valve port 21a and the second valve port 22a at a maximum flow rate to form a minimum damping force, and when the piston 2 is in the maximum stroke of the compression stroke and the maximum stroke of the extension stroke, it is ensured that the corresponding first opening 4a and the first valve port 21a are completely misaligned or nearly completely misaligned and the corresponding second opening 5a and the second valve port 22a are completely misaligned or nearly completely misaligned, so as to ensure that the oil cannot pass through or passes at a minimum flow rate. The maximum damping force is formed through the first valve port 21a and the second valve port 22a. Through such an arrangement, when the piston 2 of the shock absorber moves from the maximum stroke of the compression stroke to the maximum stroke of the extension stroke, the damping force goes through a process of first decreasing to the minimum and then increasing to the maximum. Similarly, when the piston 2 of the shock absorber moves from the maximum stroke of the extension stroke to the maximum stroke of the compression stroke, the damping force also goes through a process of first decreasing to the minimum and then increasing to the maximum, thereby ensuring that the shock absorber has extremely high damping force at the maximum stroke of the compression stroke and the maximum stroke of the extension stroke. When this shock absorber is used in the suspension system of an automobile and connected between the frame and the axle, it can improve the driving quality of the automobile, for example, provide a stable high damping force during the compression process to improve the stability of the vehicle, and also have a high damping force during the rebound process to ensure the grip of the automobile tires. In addition, if the damping force required for the maximum stroke of the shock absorber in the compression stroke is higher than the damping force required for the maximum stroke of the shock absorber in the extension stroke, it is only necessary to ensure that when the piston 2 of the shock absorber is in the maximum stroke of the compression stroke, the flow area of ​​the first valve port 21a opened by the first opening 4a and the flow area of ​​the second valve port 22a opened by the second opening 5a are smaller than the flow area of ​​the first valve port 21a opened by the first opening 4a and the flow area of ​​the second valve port 22a opened by the second opening 5a when the piston 2 of the shock absorber is in the maximum stroke of the extension stroke. Conversely, if the damping force required for the maximum stroke of the shock absorber in the compression stroke is lower than the damping force required for the maximum stroke of the shock absorber in the extension stroke, it is only necessary to ensure that when the piston 2 of the shock absorber is in the maximum stroke of the compression stroke, the flow area of ​​the first valve port 21a opened by the first opening 4a and the flow area of ​​the second valve port 22a opened by the second opening 5a are larger than the flow area of ​​the first valve port 21a opened by the first opening 4a and the flow area of ​​the second valve port 22a opened by the second opening 5a when the piston 2 of the shock absorber is in the maximum stroke of the extension stroke.

[0049] For another example, when the maximum stroke of the compression stroke of the shock absorber requires a high damping force but the maximum stroke of the extension stroke of the shock absorber does not require a high damping force, the guide structure 6 can be set to ensure that the corresponding first opening 4a and the first valve port 21a are completely misaligned or nearly completely misaligned when the piston 2 is at the maximum stroke of the compression stroke, and to ensure that the corresponding second opening 5a and the second valve port 22a are completely misaligned or nearly completely misaligned, so as to ensure that the oil cannot pass through or passes through the first valve port 21a and the second valve port 22a at a minimum flow rate to form the maximum damping force, and when the piston 2 is at the maximum stroke of the extension stroke, to ensure that the corresponding The first opening 4a and the first valve port 21a are fully aligned and the corresponding second opening 5a and the second valve port 22a are fully aligned, thereby ensuring that the oil passes through the first valve port 21a and the second valve port 22a at a maximum flow rate to form a minimum damping force. Through such a setting, when the piston 2 of the shock absorber moves from the maximum stroke of the compression stroke to the maximum stroke of the tension stroke, the damping force undergoes a process of gradually decreasing. Conversely, when the piston 2 of the shock absorber moves from the maximum stroke of the tension stroke to the maximum stroke of the compression stroke, the damping force undergoes a process of gradually increasing, thereby ensuring that the maximum stroke of the compression stroke of the shock absorber has a high damping force.

[0050] For another example, when the maximum stroke of the stretching stroke of the shock absorber requires a high damping force but the maximum stroke of the compression stroke of the shock absorber does not require a high damping force, the guide structure 6 can be set to ensure that the corresponding first opening 4a and the first valve port 21a are completely misaligned or nearly completely misaligned when the piston 2 is at the maximum stroke of the stretching stroke, and to ensure that the corresponding second opening 5a and the second valve port 22a are completely misaligned or nearly completely misaligned, so as to ensure that the oil cannot pass through or passes through the first valve port 21a and the second valve port 22a at a minimum flow rate to form the maximum damping force, and when the piston 2 is at the maximum stroke of the compression stroke, to ensure that the corresponding The first opening 4a and the first valve port 21a are fully aligned and the corresponding second opening 5a and the second valve port 22a are fully aligned, thereby ensuring that the oil passes through the first valve port 21a and the second valve port 22a at a maximum flow rate to form a minimum damping force. Through such a setting, when the piston 2 of the shock absorber moves from the maximum stroke of the stretching stroke to the maximum stroke of the compression stroke, the damping force undergoes a process of gradually decreasing. On the contrary, when the piston 2 of the shock absorber moves from the maximum stroke of the compression stroke to the maximum stroke of the stretching stroke, the damping force undergoes a process of gradually increasing, thereby ensuring that the maximum stroke of the stretching stroke of the shock absorber has a high damping force.

[0051] In the above, the shape of the corresponding first opening 4a and the shape of the first valve port 21a are preferably compatible shapes, and the shape of the corresponding second opening 5a and the shape of the second valve port 22a are preferably compatible shapes, so as to ensure the flow of oil when the first opening 4a is fully aligned with the first valve port 21a and to ensure the flow of oil when the second opening 5a is fully aligned with the second valve port 22a.

[0052] In a preferred embodiment, Figures 4 to 7 As shown, the guide structure 6 includes a first guide member 61 arranged on the first flow regulating valve 4, a second guide member 62 arranged on the second flow regulating valve 5, and a spiral guide groove 63 formed on the inner wall of the cylinder 1, and the first guide member 61 and the second guide member 62 are both guided and matched with the spiral guide groove 63. Specifically, the rotation speed of the first flow regulating valve 4 relative to the first valve structure 21 and the rotation speed of the second flow regulating valve 5 relative to the second valve structure 22 in the compression stroke and the extension stroke of the shock absorber can be determined by setting the size of the spiral angle of the spiral guide groove 63. For example, when the spiral angle of the spiral guide groove 63 is small, the rotation speed of the first flow regulating valve 4 relative to the first valve structure 21 and the rotation speed of the second flow regulating valve 5 relative to the second valve structure 22 are slower when the shock absorber is in the compression stroke and the extension stroke, and when the spiral angle of the spiral guide groove 63 is large, the rotation speed of the first flow regulating valve 4 relative to the first valve structure 21 and the rotation speed of the second flow regulating valve 5 relative to the second valve structure 22 are faster when the shock absorber is in the compression stroke and the extension stroke. It should be noted that the helix angle refers to the angle between the tangent of the helix line and the axis of the thread on the mid-diameter cylindrical surface. The helix angle and the helix lead angle (the helix lead angle refers to the angle between the tangent of the helix line and the plane perpendicular to the axis of the thread on the mid-diameter cylindrical surface) are complementary.

[0053] Alternatively, if Figures 4 to 7As shown, the first guide member 61 includes a first guide bead 611 and a first spring 612 connecting the first guide bead 611 to the first flow regulating valve 4, and the first guide bead 611 is slidably set in the spiral guide groove 63. The second guide member 62 includes a second guide bead 621 and a second spring 622 connecting the second guide bead 621 to the second flow regulating valve 5, and the second guide bead 621 is slidably set in the spiral guide groove 63. Through the same spiral guide groove 63, the first flow regulating valve 4 and the second flow regulating valve 5 of the shock absorber can rotate together in the compression stroke and the extension stroke, so as to adjust the flow area of ​​the first opening 4a to open the first valve port 21a and the flow area of ​​the second opening 5a to open the second valve port 22a. The first spring 612 allows the first guide bead 611 to produce a certain amount of deformation when it is guided with the spiral guide groove 63, which can not only ensure the rotation of the first flow control valve 4 relative to the first valve structure 21, but also make the guiding cooperation of the first guide bead 611 and the spiral guide groove 63 non-pure rigid connection, so as to avoid the first guide bead 611 and the spiral guide groove 63 from being greatly worn after long-term use, thus affecting the service life of the shock absorber. Similarly, the second spring 622 allows the second guide bead 621 to produce a certain amount of deformation when it is guided with the spiral guide groove 63, which can not only ensure the rotation of the second flow control valve 5 relative to the second valve structure 22, but also make the guiding cooperation of the second guide bead 621 and the spiral guide groove 63 non-pure rigid connection, thus avoiding the second guide bead 621 and the spiral guide groove 63 from being greatly worn after long-term use, thus affecting the service life of the shock absorber. Of course, in the above, as an alternative, the first spring 612 and the second spring 622 can also be eliminated, that is, the first guide bead 611 is directly connected to the first flow regulating valve 4, and the second guide bead 621 is directly connected to the second flow regulating valve 5. In addition, the first guide member 61 and the second guide member 62 can also adopt other structures that can achieve guidance, and technical personnel in this field can flexibly arrange this.

[0054] As an alternative, in the above, in addition to using one spiral guide groove 63 to guide the first guide member 61 and the second guide member 62 together, two spiral guide grooves can also be used to guide the first guide member 61 and the second guide member 62 respectively. Specifically, as shown in FIG. Figures 6 to 8As shown, the guide structure 6 includes a first guide member 61 provided on the first flow regulating valve 4, a second guide member 62 provided on the second flow regulating valve 5, and a first spiral guide groove 63a and a second spiral guide groove 63b formed on the inner wall of the cylinder 1, the first guide member 61 is guided and matched with the first spiral guide groove 63a, and the second guide member 62 is guided and matched with the second spiral guide groove 63b. Specifically, the rotation speed of the first flow regulating valve 4 relative to the first valve structure 21 in the compression stroke and the extension stroke of the shock absorber can be determined by setting the size of the spiral angle of the first spiral guide groove 63a, and the rotation speed of the second flow regulating valve 5 relative to the second valve structure 22 in the compression stroke and the extension stroke of the shock absorber can be determined by setting the size of the spiral angle of the second spiral guide groove 63b. Taking the first spiral guide groove 63a as an example, when the spiral angle of the first spiral guide groove 63a is small, the rotation speed of the first flow regulating valve 4 relative to the first valve structure 21 is slower when the shock absorber is in the compression stroke and the extension stroke, and when the spiral angle of the first spiral guide groove 63a is large, the rotation speed of the first flow regulating valve 4 relative to the first valve structure 21 is faster when the shock absorber is in the compression stroke and the extension stroke. Taking the second spiral guide groove 63b as an example, when the spiral angle of the second spiral guide groove 63b is small, the rotation speed of the second flow regulating valve 5 relative to the second valve structure 22 is slower when the shock absorber is in the compression stroke and the extension stroke, and when the spiral angle of the second spiral guide groove 63b is large, the rotation speed of the second flow regulating valve 5 relative to the second valve structure 22 is faster when the shock absorber is in the compression stroke and the extension stroke. Through such an arrangement, the guide rotation of the first flow regulating valve 4 and the flow control of the first valve structure 21 as well as the guide rotation of the second flow regulating valve 5 and the flow control of the second valve structure 22 are independent of each other. The advantage of such an arrangement is that the first spiral guide groove 63a and the second spiral guide groove 63b with different spiral angles can be set, so that when the shock absorber is in the compression stroke and the extension stroke, the rotation speed of the first flow regulating valve 4 relative to the first valve structure 21 and the rotation speed of the second flow regulating valve 5 relative to the second valve structure 22 are different, thereby providing more possibilities for the design of the change of damping force.

[0055] Alternatively, if Figures 6 to 8As shown, the first guide member 61 includes a first guide bead 611 and a first spring 612 connecting the first guide bead 611 with the first flow control valve 4, the first guide bead 611 is slidably disposed in the first spiral guide groove 63a, and the second guide member 62 includes a second guide bead 621 and a second spring 622 connecting the second guide bead 621 with the second flow control valve 5, the second guide bead 621 is slidably disposed in the second spiral guide groove 63b. The first spring 612 allows the first guide bead 611 to produce a certain amount of deformation when guiding and cooperating with the first spiral guide groove 63a, which can not only ensure the rotation of the first flow control valve 4 relative to the first valve structure 21, but also make the guiding cooperation of the first guide bead 611 and the first spiral guide groove 63a non-pure rigid connection, so as to avoid the first guide bead 611 and the first spiral guide groove 63a from being greatly worn after long-term use, thereby affecting the service life of the shock absorber. Similarly, the second spring 622 allows the second guide bead 621 to produce a certain amount of deformation when guiding and cooperating with the second spiral guide groove 63b, which can not only ensure the rotation of the second flow control valve 5 relative to the second valve structure 22, but also make the guiding cooperation of the second guide bead 621 and the second spiral guide groove 63b non-pure rigid connection, so as to avoid the second guide bead 621 and the second spiral guide groove 63b from being greatly worn after long-term use, thereby affecting the service life of the shock absorber. Of course, in the above, as an alternative, the first spring 612 and the second spring 622 can also be eliminated, that is, the first guide bead 611 is directly connected to the first flow control valve 4, and the second guide bead 621 is directly connected to the second flow control valve 5.

[0056] In the above, if Figure 1 , 4 As shown in FIGS. 5 and 8, whether a single spiral guide groove 63 is used or the first spiral guide groove 63a and the second spiral guide groove 63b are used respectively, when the cylinder wall of the cylinder barrel 1 is relatively thin, the cylinder wall of the cylinder barrel 1 can be made to protrude outward to form a single spiral guide groove 63 or the first spiral guide groove 63a and the second spiral guide groove 63b.

[0057] In addition, in addition to the aforementioned guide structure 6 that cooperates with the spiral guide groove 63 through the guide member, other forms of guide structures 6 can also be used, as long as the guide structure 6 can achieve a change in the damping force when the shock absorber is in different stroke positions of the compression stroke and the extension stroke.

[0058] In the present invention, the first flow regulating valve 4 is rotatably arranged on the first valve structure 21, and the first flow regulating valve 4 can be sleeved on the first valve structure 21 and located between the cylinder 1 and the first valve structure 21, thereby saving the axial dimension of the cylinder 1, and only the radial dimension of the cylinder 1 needs to be appropriately increased. Of course, the first flow regulating valve 4 is rotatably arranged on the first valve structure 21, and the first flow regulating valve 4 and the first valve structure 21 can be stacked along the axial direction of the cylinder 1, that is, the first flow regulating valve 4 is located between the first valve structure 21 and the first chamber 11. Similarly, the second flow regulating valve 5 is rotatably arranged on the second valve structure 22, and the second flow regulating valve 5 can be sleeved on the second valve structure 22 and located between the cylinder 1 and the second valve structure 22, thereby saving the axial dimension of the cylinder 1, and only the radial dimension of the cylinder 1 needs to be appropriately increased. Of course, the second flow regulating valve 5 is rotatably arranged on the second valve structure 22, and the second flow regulating valve 5 and the second valve structure 22 can be stacked along the axial direction of the cylinder 1, that is, the second flow regulating valve 5 is located between the second valve structure 22 and the second chamber 12.

[0059] In the above-mentioned case where the first flow regulating valve 4 is sleeved on the first valve structure 21 and is located between the cylinder 1 and the first valve structure 21, and the second flow regulating valve 5 is sleeved on the second valve structure 22 and is located between the cylinder 1 and the second valve structure 22, it is preferred that the shape of the first valve structure 21 and the shape of the first flow regulating valve 4 are both annular, a plurality of first valve ports 21a are arranged in annular distribution on the first valve structure 21, a plurality of first openings 4a are arranged in annular distribution on the first flow regulating valve 4, the shape of the second valve structure 22 and the shape of the second flow regulating valve 5 are both annular, a plurality of second valve ports 22a are arranged in annular distribution on the second valve structure 22, and a plurality of second openings 5a are arranged in annular distribution on the second flow regulating valve 5. Among them, those skilled in the art can flexibly set the number of the first valve ports 21a, the first openings 4a, the second valve ports 22a and the second openings 5a. For example, in one possible case, the number of the first valve ports 21a, the first openings 4a, the second valve ports 22a and the second openings 5a are all 6.

[0060] In the present invention, as described above, in the case where the first valve structure 21 and the second valve structure 22 are connected through the valve plate group 23, the valve plates can be superimposed on each other to form pores, so as to ensure that the valve plate group 23 can generate a damping force on the oil, and the damping force is generated by the friction between the hole wall and the oil and the friction between the liquid molecules. It should be noted that when the first flow regulating valve 4, the second flow regulating valve 5 and the guide structure 6 are not added, the amount of oil flowing through the valve plate group 23 is a constant value, that is, a constant damping force is formed. In a possible situation, as Figure 5As shown, the first valve structure 21 has a flow channel connected to all the first valve ports 21a, and the flow channel can be one or more. The valve plate matched with the first valve structure 21 can be a semicircular valve plate or a major arc bow valve plate (the major arc bow is a shape surrounded by a major arc and a chord), thereby exposing part of a flow channel or part of the flow channel, allowing oil to pass through the first valve structure 21. Similarly, the second valve structure 22 has a flow channel connected to all the second valve ports 22a. The valve plate matched with the second valve structure 22 can be a semicircular valve plate or a major arc bow valve plate, thereby exposing part of a flow channel or part of the flow channel, allowing oil to pass through the second valve structure 22. The inner wall of the channel (i.e., the channel not blocked by the valve plate) formed by the first valve structure 21 and the second valve structure 22 that allows oil to pass through generates friction with the oil. At the same time, the friction between the oil molecules together forms a damping force, so that the shock absorber plays a vibration reduction role, as shown in FIG. Figure 5 As shown, when the shock absorber is in the extension stroke, the piston 2 of the shock absorber moves up along the arrow direction shown outside the cylinder 1 in the figure, and the oil flows from the first chamber 11 to the second chamber 12 through the arrow direction in the cylinder 1 in the figure. When the shock absorber is in the compression stroke, the piston 2 of the shock absorber moves down along the direction shown in the figure, and the oil flows from the second chamber 12 to the first chamber 11 in the opposite direction of the arrow direction in the cylinder 1 in the figure. The shape and number of each valve plate in the above-mentioned valve plate group 23 can be flexibly set according to the damping force required to be provided. For example, the thickness of the valve plate can be only 1mm, and the axial position of all valve plates can be maintained by an elastic member such as a spring. Alternatively, in another possible situation, as Fig. 9 As shown, the valve plate group 23 can also use a plurality of circular valve plates with exactly the same structure, and a plurality of through holes arranged in an annular manner are formed on the circular valve plates. All the circular valve plates are stacked in an axial direction, and each two adjacent circular valve plates are staggered in a circumferential direction so that the corresponding through holes on all the circular valve plates form a spiral channel 23a in the axial direction (actually there are a plurality of spiral channels 23a, Fig. 9 The advantage of forming the spiral channel 23a is that the damping path can be extended, and the damping force can be increased by the friction between the through hole wall and the oil and the friction between the liquid molecules. As an alternative, in another possible situation, as Fig.10 As shown, the valve plate has a certain thickness, and the valve plate has a plurality of one-way valves distributed in an annular manner. Fig.10There are 6 one-way valves shown in the figure, and the directions of each two adjacent one-way valves are opposite. For example, there are 3 first one-way valves 23b on the valve plate that only allow the oil to flow from the first chamber 11 to the second chamber 12, and there are 3 second one-way valves 23c on the valve plate that only allow the oil to flow from the second chamber 12 to the first chamber 11, so that the valve plate of the valve plate group 23 of the shock absorber has a corresponding one-way valve to allow the oil to flow through whether it is in the compression stroke or the extension stroke. The friction between the inner wall of the channel of the one-way valve and the oil and the friction between the liquid molecules increase the damping force. It should be noted that the present invention can design different types of valve plate groups 23 according to different needs or adjust the specific structure of the valve plate to achieve the initial setting of the fixed damping force, and then add the first flow regulating valve 4, the second flow regulating valve 5 and the guide structure 6 to design the change of the damping force under different strokes, that is, on the basis of the initial set fixed damping force, further design the increased damping force according to the stroke to achieve passive adjustment of the damping force.

[0061] The present invention also provides a car, comprising the aforementioned shock absorber, which can be used in the suspension system of the car and can also be used in other positions of the car.

[0062] So far, the technical solutions of the present invention have been described in conjunction with the preferred embodiments shown in the accompanying drawings. However, it is easy for those skilled in the art to understand that the protection scope of the present invention is obviously not limited to these specific embodiments. Without departing from the principle of the present invention, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after these changes or substitutions will fall within the protection scope of the present invention.

Claims

1. A passive adjustable damping force shock absorber, characterized in that: The shock absorber comprises a cylinder (1), a piston (2) capable of moving in the cylinder (1), and a piston rod (3) whose inner end is connected to the piston (2); the piston (2) divides the internal chamber of the cylinder (1) into a first chamber (11) and a second chamber (12); the piston (2) comprises a first valve structure (21) and a second valve structure (22) which are connected to each other; the first valve structure (21) is formed with a plurality of first valve ports (21a) which are connected to the first chamber (11); the second valve structure (22) is formed with a plurality of second valve ports (22a) which are connected to the second chamber (12); The shock absorber further comprises a first flow regulating valve (4), a second flow regulating valve (5) and a guide structure (6); the first flow regulating valve (4) is rotatably arranged on the first valve structure (21); the second flow regulating valve (5) is rotatably arranged on the second valve structure (22); the first flow regulating valve (4) is formed with a first opening (4a) corresponding to the first valve port (21a) in a one-to-one manner; the second flow regulating valve (5) is formed with a second opening (5a) corresponding to the second valve port (22a) in a one-to-one manner; the guide structure (6) is arranged to be able to adjust the flow rate of the shock absorber during the compression stroke and the During the stretching stroke, the first flow regulating valve (4) is rotated relative to the first valve structure (21) to change the relative position of the corresponding first opening (4a) and the first valve port (21a), thereby changing the flow area between the first opening (4a) and the first chamber (11); and the second flow regulating valve (5) is rotated relative to the second valve structure (22) to change the relative position of the corresponding second opening (5a) and the second valve port (22a), thereby changing the flow area between the second valve port (22a) and the second chamber (12), thereby adjusting the damping force of the shock absorber itself.

2. The passive adjustable damping force shock absorber according to claim 1, characterized in that: The guide structure (6) comprises a first guide member (61) arranged on the first flow regulating valve (4), a second guide member (62) arranged on the second flow regulating valve (5), and a spiral guide groove (63) formed on the inner wall of the cylinder (1), and the first guide member (61) and the second guide member (62) are both guided and matched with the spiral guide groove (63).

3. The passive adjustable damping force shock absorber according to claim 2, characterized in that: The first guide member (61) comprises a first guide bead (611) and a first spring (612) connecting the first guide bead (611) to the first flow regulating valve (4), the first guide bead (611) being slidably disposed in the spiral guide groove (63); and / or The second guide member (62) comprises a second guide bead (621) and a second spring (622) connecting the second guide bead (621) to the second flow regulating valve (5), and the second guide bead (621) is slidably disposed in the spiral guide groove (63).

4. The passive adjustable damping force shock absorber according to claim 1, characterized in that: The guide structure (6) comprises a first guide member (61) arranged on the first flow regulating valve (4), a second guide member (62) arranged on the second flow regulating valve (5), and a first spiral guide groove (63a) and a second spiral guide groove (63b) formed on the inner wall of the cylinder (1), wherein the first guide member (61) is in guiding cooperation with the first spiral guide groove (63a), and the second guide member (62) is in guiding cooperation with the second spiral guide groove (63b).

5. The passive adjustable damping force shock absorber according to claim 4, characterized in that: The first guide member (61) includes a first guide bead (611) and a first spring (612) connecting the first guide bead (611) to the first flow regulating valve (4), and the first guide bead (611) is slidably disposed in the first spiral guide groove (63a). The second guide member (62) includes a second guide bead (621) and a second spring (622) connecting the second guide bead (621) to the second flow regulating valve (5), and the second guide bead (621) is slidably disposed in the second spiral guide groove (63b).

6. The passive adjustable damping force shock absorber according to claim 1, characterized in that: The first flow regulating valve (4) is sleeved on the first valve structure (21) and is located between the cylinder (1) and the first valve structure (21). The second flow regulating valve (5) is sleeved on the second valve structure (22) and is located between the cylinder (1) and the second valve structure (22).

7. The passive adjustable damping force shock absorber according to claim 6, characterized in that: The shape of the first valve structure (21) and the shape of the first flow regulating valve (4) are both annular, the multiple first valve ports (21a) are arranged in annular distribution on the first valve structure (21), and the multiple first openings (4a) are arranged in annular distribution on the first flow regulating valve (4).

8. The passive adjustable damping force shock absorber according to claim 6, characterized in that: The shape of the second valve structure (22) and the shape of the second flow regulating valve (5) are both annular, the multiple second valve ports (22a) are arranged in annular distribution on the second valve structure (22), and the multiple second openings (5a) are arranged in annular distribution on the second flow regulating valve (5).

9. The passive adjustable damping force vibration absorber according to any one of claims 1 to 8, characterized in that: The first valve structure (21) and the second valve structure (22) are in communication with each other via a valve plate group (23).

10. An automobile, characterized in that: The automobile comprises the passive adjustable damping force shock absorber according to any one of claims 1 to 9.

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