Negative stiffness damper and performance calibration method and selection and matching method therefor, and vehicle using damper

Abstract

The present invention provides a damper having negative stiffness, comprising: a cylinder barrel, a piston rod, a piston, and a base valve. A rebound valve and a check valve are provided on the piston; a compression valve and a check valve are provided on the base valve; a valve core of the compression valve is connected to a valve core of the rebound valve by means of a spring; a limiting device for the valve core of the rebound valve is provided on the piston or the piston rod; and damping force values of the compression valve and the rebound valve are both controlled by the stroke of the piston and the acting force of the spring. During the extension of the damper, when the spring is in a compressed state, the rebound valve forms a damping force, thereby achieving a damping effect. The greater a compression stroke (compression force value) of the spring is, the greater the extension damping value of the damper is. During the compression of the damper, when the spring is in a tensioned state, the compression valve creates a damping force, thereby achieving a damping effect. The greater an extension stroke (extension force value) of the spring is, the greater the compression damping value of the damper is.

Description

A negative stiffness vibration damper, its performance specification method and selection and matching method, and a vehicle using this vibration damper. Technical Field

[0001] This invention relates to the field of vibration dampers, and is particularly applicable to single-tube or twin-tube vibration dampers. Background Technology

[0002] The damping force of commonly used hydraulic cylinder damper tension valves and compression damping valves is usually related to the tension or compression speed of the damper; that is, the faster the tension or compression speed, the greater the damping, and the slower the tension or compression speed, the smaller the damping. A small number of high-performance active dampers adjust their damping force in real time by measuring the road surface undulations in front of the vehicle. However, their damping force cannot be accurately controlled according to the actual stress conditions of the vehicle.

[0003] Existing shock absorbers typically use dynamometer diagrams to represent their performance. This method cannot accurately reflect the shock absorption performance of the shock absorber, and there is no specific matching method between the shock absorber and the vehicle support spring (23) to guide the selection relationship between the shock absorber and the support spring (23).

[0004] In addition, commonly used shock absorbers require both tension fluid flow channels and compression fluid flow channels (one-way valve channels) to be set on the piston, resulting in a small installation space and effective diameter for the one-way valve. During rapid compression, the fluid velocity is high, and the damping of the fluid entering the rod chamber through the one-way valve is too large, thus forming a cavitation effect, which greatly affects the damping effect of the shock absorber. Technical issues

[0005] The technical problem solved by this invention:

[0006] 1. Solve the problem that the vibration damping performance of vibration dampers lacks quantitative standards and cannot be quantified.

[0007] 2. Solve the problem of matching the performance of shock absorbers with support springs and vehicle loads.

[0008] 3. To link the tensile and compressive damping force values ​​of the shock absorber with the tensile or compressive stroke of the shock absorber, thereby achieving the effect of automatically adjusting the damping force value of the shock absorber.

[0009] 4. Provide a vibration damper structure solution that is simple in structure and has better performance.

[0010] 5. Reduce the impact of the speed of the shock absorber during tension or compression on the damping value of the shock absorber, so as to make the shock absorber perform better.

[0011] 6. For a long time, vibration damper technicians have used the extension and contraction speed and vibration (extension) frequency of the vibration damper as the basis for adjusting the damping force value. This invention uses the extension stroke position or compression stroke position of the vibration damper as the main basis for controlling the damping force value, overcoming the bias of the traditional method that uses speed and vibration damper extension and contraction frequency as the basis for controlling the damping force value.

[0012] 7. The shock absorber in this solution can provide a shock absorber with negative stiffness damping characteristics whose absolute stiffness is equal to or similar to the stiffness of the vehicle support spring.

[0013] 8. Allowing a portion of the tension fluid flow channel and the compression fluid flow channel (one-way valve channel) at the rod end of the shock absorber piston to be shared effectively increases the fluid flow path into the rod chamber and reduces the fluid flow damping into the rod, thus avoiding or reducing cavitation effects caused by insufficient fluid supply.

[0014] 9. Effectively overcomes the influence of temperature changes on the damping value of the shock absorber, so that the damping force value of the shock absorber is not affected by temperature changes. Technical solutions

[0015] Option A: A shock absorber includes components such as a cylinder, piston rod, piston, check valve, tension valve, and compression valve. When a tension valve is provided, it is mounted on the piston; when a compression valve is provided, it is mounted on the bottom valve. In this option, a spring is provided in the rodless chamber of the cylinder, and the spring end is connected to the tension valve (9) or compression valve (19). The spring force controls the damping force of the tension valve or compression valve. This controls the damping force of the tension valve (9) or compression valve (19) of the shock absorber, so that when the shock absorber is in a tension state and the spring is compressed, it has a negative stiffness tension damping coefficient; or when the shock absorber is in a compression state and the spring is stretched, it has a negative stiffness compression damping coefficient. When the damper is stretched or compressed, the piston moves upward to stretch or downward to compress, causing the spring to bear tension or pressure. The tension or pressure of the spring (13) changes with the position of the piston. The tension or pressure of the spring is loaded on the compression valve or the tension valve, controlling the damping force value of the tension valve (9) or the compression valve (19) of the damper, thereby forming a tensile damping force or a compression damping force with a negative stiffness coefficient, so that the damper has a damping force value that corresponds one-to-one with the stroke position of the damper. When the piston moves upward to stretch or downward to compress, the change in distance between the piston and the bottom of the cylinder controls the stretching or compression of the spring (13). The change in the stretching or compression of the spring, in turn, controls the damping force of the stretching or compression valve of the damper. This makes the stretching or compression damping force of the damper proportional to the piston stroke within a set range (the set range refers to the stroke range of L1~L2, L2~L3, L3~L4 in Figures 5, 8, and 9, and some values ​​of this stroke range can be set by changing the free length of the spring). That is, the stretching damping force of the damper is proportional to the compression force of the spring, or the compression damping force of the damper is proportional to the stretching force of the spring. The damper has a one-to-one corresponding stretching or compression damping force at any stroke position.

[0016] The damping force of this shock absorber changes with the position of the shock absorber's stroke, and its damping force is basically unaffected by the shock absorber's tensile or compressive speed.

[0017] The terms "upward" and "downward" in this text are merely illustrative of the illustrations in this patent to facilitate understanding and do not limit the actual positional relationship of the shock absorber during operation. That is, the downward movement of the piston corresponds to the compression process of the shock absorber, and the upward movement of the piston corresponds to the extension process of the shock absorber.

[0018] Generally, the free length of the spring (13) should be less than the stroke of the damper.

[0019] Option B, as described in Option A, includes: a cylinder, a piston rod, a piston, a one-way valve on the piston, and a valve hole on the piston that cooperates with the valve core of the tension valve. The valve hole communicates with the rod chamber. The valve core of the tension valve is placed in the rodless chamber. A spring is provided between the valve core and the bottom of the cylinder or the bottom valve. During the tensioning process of the damper, when the spring (13) is compressed, the valve core and the valve hole of the tension valve form a tension damping valve under the action of the compression force of the spring (13). During the tensioning process of the damper, when the spring (13) is in a compressed state, the tension valve forms a damping force, achieving the damping effect. The larger the compression stroke (compression force value) of the spring (13), the greater the tension damping value of the damper. When the spring (13) is in a non-compressed state, the tension valve opens, and the tension damping value is the minimum. During the compression process of the damper, the fluid flow in the rodless chamber mainly enters the rod chamber through the one-way valve on the piston. The damper of this option can be equipped with a bottom valve or not.

[0020] The connection between the spring (13) and the valve core, and between the spring (13) and the bottom of the cylinder or the foot valve, is unrestricted, and the connection method is also unrestricted. That is, a fixed connection, a non-fixed connection, or a single-head fixed connection can be used.

[0021] Working principle: As shown in Figure 1 and Figure 2, the valve core of the tension valve is subjected to the force of the spring (13) and cooperates with the valve hole to form a tension damping valve. During the process of the piston moving from L1 to L2, the spring (13) transitions from the compressed state to the free state, and the damping of the tension damping valve decreases from large to small, that is, the tension damping force of the shock absorber decreases from large to small.

[0022] When the piston moves up to position L2 (spring (13) free length position), the damping reaches its minimum value until the piston moves up to position L3. When the piston moves down, the fluid flows from the rodless chamber to the rod chamber through the one-way valve on the piston.

[0023] Option C, as described in Option A, includes: a cylinder, a piston rod, a piston, a bottom valve, and a compression valve and a check valve on the bottom valve. The valve core of the compression valve is connected to the piston or piston rod via a spring (13), so that the damping force of the compression valve is controlled by the piston stroke and the tension of the spring (13). During the compression process of the damper, when the spring (13) is in tension, the compression valve generates a damping force, achieving the damping effect. The greater the tension stroke (tension force) of the spring (13), the greater the compression damping value of the damper. When the spring (13) is in a free state and a compressed state, the compression valve of the damper is open, and the compression damping is at its minimum. The piston or piston rod in this option can be replaced by a plunger.

[0024] Working principle:

[0025] As shown in Figure 2: The compression valve core, under the tension of the spring (13), cooperates with the compression valve orifice to form a damping valve. During the process of the piston moving down from position L4 to position L3, the spring (13) transitions from a stressed state to a free state, and the damping force of the damping valve decreases, that is, the compression damping force of the shock absorber decreases. When the piston moves down to position L3 (the free length position of the spring (13)), the damping reaches its minimum value until the piston moves down to position L1. When the piston moves down from position L2 to position L1, the spring (13) is compressed, the compression valve core is located at the bottom of the valve, and the compression valve is in the fully open state.

[0026] Option D: The shock absorber as described in Option A includes: a cylinder, a piston rod, a piston, a bottom valve, a tension valve and a check valve on the piston, a compression valve and a check valve on the bottom valve, the valve core of the tension valve being connected to the valve core of the compression valve via a spring (13), and a limiting device for restricting the stroke of the tension valve core being provided on the piston or piston rod. The limiting device can be a nut, a pin, a ring, etc. During the compression process of the shock absorber, when the spring (13) is stretched, the damping force of the compression valve is controlled by the stroke of the piston and the tension force of the spring (13); during the stretch process of the shock absorber, when the spring (13) is compressed, the damping force of the tension valve is controlled by the stroke of the piston and the compression force of the spring (13).

[0027] During the stretching process of the damper, when the spring (13) is under compression, the stretching valve generates a damping force, achieving the damping effect. The greater the compression stroke (compression force value) of the spring (13), the greater the stretching damping value of the damper. During the compression process of the damper, when the spring (13) is under tension, the compression valve generates a damping force, achieving the damping effect. The greater the stretching stroke (tension force value) of the spring (13), the greater the compression damping value of the damper.

[0028] Working principle: As shown in Figure 3:

[0029] When the piston compresses downwards, the valve core of the compression valve is pulled by the spring (13) and cooperates with the valve orifice of the compression valve to form a damping valve. During the process of the piston moving down from position L4 to position L3, the spring (13) transitions from a stressed state to a free state, and the damping force of the damping valve decreases, that is, the compression damping force of the shock absorber decreases. When the piston moves down to position L3 (the free length position of the spring (13)), the damping reaches its minimum value until the piston moves down to position L1. When the piston moves down from position L2 to position L1, the spring (13) is compressed, the valve core of the compression valve is located at the bottom of the valve, and the compression valve is in the fully open state.

[0030] When the piston is pulled upwards, the valve core of the tension valve is subjected to the force of the spring (13) and cooperates with the valve hole to form a damping valve. During the process of the piston moving upwards from L1 to L2, the spring (13) transitions from a compressed state to a free state, and the damping of the tension damping valve decreases, that is, the tension damping force of the shock absorber decreases. When the piston moves upwards to L2 (the free length position of the spring (13)), the damping reaches the minimum value until the piston moves upwards to L4.

[0031] When the piston moves downward, the fluid flows from the rodless chamber to the rod chamber through the one-way valve on the piston.

[0032] When the piston moves upward, the liquid in the reservoir flows into the rodless chamber of the cylinder through the one-way valve on the bottom valve.

[0033] The theoretical damping value of the aforementioned (Figure 3) shock absorber is calculated as follows:

[0034] The calculation methods for theoretical tensile damping and tensile stiffness in the above scheme are as follows:

[0035]

[0036]

[0037] Theoretical methods for calculating compressive damping and compressive stiffness:

[0038]

[0039]

[0040] F 拉实 =F 支 + F 拉

[0041] F 压实 =F 支 + F 压

[0042] F 拉 Real-time tensile damping force value of the vibration damper

[0043] K 拉 The tensile damping stiffness value of the vibration damper

[0044] F 压 The real-time compressive damping force value of the shock absorber

[0045] K 压 The compression damping stiffness value of the vibration damper

[0046] S1 is the cross-sectional area of ​​the hydraulic cylinder.

[0047] S2 is the cross-sectional area of ​​the piston rod.

[0048] S3 is the effective cross-sectional area of ​​the tension valve orifice.

[0049] S4 is the effective cross-sectional area of ​​the compression valve orifice.

[0050] F 支 To support the real-time force value of spring (23)

[0051] K 内 Stiffness of the spring (13) inside the shock absorber

[0052] F 拉实 The real-time support force on the vehicle caused by the combined force of the shock absorber and the support spring during the shock absorber's extension stroke.

[0053] F 压实 This refers to the real-time support force exerted on the vehicle by the combined force of the shock absorber and the support spring during the shock absorber's compression stroke.

[0054] F 目 Target support force value

[0055] Explanation of the stroke position of the shock absorber:

[0056] L1 Shock absorber compression stroke limit position

[0057] L2 is the critical position of the free length of the compression stroke spring (critical position for sealing of the tension valve).

[0058] L3 is the critical position of the free length of the tension stroke spring (critical position for compression valve sealing).

[0059] L4 shock absorber extension stroke limit position

[0060] L X Any real-time position of the damper during tension or compression

[0061] L1~L2 Effective stroke range for tensile damping negative stiffness and compressive resistance positive stiffness

[0062] L2~L3 Minimum stroke range for tensile and compressive damping

[0063] L3~L4 Effective stroke range for negative stiffness of compression damping and positive stiffness of tension damping

[0064] In Figure 8, S represents the corresponding stroke position, and F represents the magnitude of the vector force.

[0065] Methods for representing the performance of vibration dampers

[0066] The damping performance of a vibration damper is represented by the stiffness values ​​corresponding to each position in its tensile and compressive strokes, or by the positions corresponding to each stiffness value. The stiffness values ​​of a vibration damper include tensile stiffness and compressive stiffness, with each stroke segment corresponding to its own stiffness value.

[0067] In the compression stiffness value of a vibration damper, a negative stiffness value indicates that the larger the compression stroke, the smaller the compression force; in the tensile stiffness value of a vibration damper, a negative stiffness value indicates that the larger the tensile stroke, the smaller the tensile force.

[0068] like:

[0069] The tensile damping stiffness value for the stretching strokes L1~L2 is -nkgf / cm;

[0070] The tensile damping stiffness value for the stretching strokes L3~L4 is nkgf / cm;

[0071] The compression damping stiffness value for the compression strokes L1~L2 is nkgf / cm;

[0072] The compression damping stiffness value for the compression strokes L3~L4 is -nkgf / cm;

[0073] The stiffness value of the transition stroke L2~L3 is nkgf / cm;

[0074] In -nkgf / cm, n represents the actual numerical value. For example, -5kgf / cm means that for every 1 cm increase in the stretching stroke of L1~L2 in the stretching direction, the stretching damping is reduced by 5 kg of stretching force.

[0075] Other performance representation methods can also be used. Any method that can represent the stiffness performance of the vibration damper and the relationship between each stiffness and position is considered an equivalent representation method.

[0076] The vibration damper can be adjusted by changing the cross-sectional area of ​​S1~S4, K 内 Different vibration damping performances are set by adjusting the stiffness of the spring (13) and the free length of the spring (13).

[0077] Matching method between shock absorber and support spring (23):

[0078] 1. Stiffness value matching method

[0079] Within all stroke ranges where the support force of the support spring (23) on the vehicle is less than the target support force value, the better the damping effect is, the closer the absolute value of the compression stiffness of the damper within this stroke range is to the stiffness value of the equivalent support spring (23); that is, the matching standard is that the absolute value of the compression stiffness of the damper (22) within this stroke range is equal to or close to the stiffness value of the equivalent support spring (23).

[0080] Within all stroke ranges where the support force of the support spring (23) on the vehicle exceeds the target support force value, the better the damping effect is, the closer the absolute value of the tensile stiffness of the damper within this stroke range is to the stiffness value of the equivalent support spring (23); that is, the matching standard is that the absolute value of the tensile stiffness of the damper (22) within this stroke range is equal to or close to the stiffness value of the equivalent support spring (23).

[0081] When the supporting force of the support spring (23) on the vehicle is close to the target supporting force value, the smaller the absolute values ​​of the compression stiffness, tension stiffness, and damping value of the shock absorber, the better. That is, the minimum values ​​that the absolute values ​​of the compression stiffness, tension stiffness, and damping of the shock absorber (22) can be achieved are used as the matching standard.

[0082] Within all stroke ranges where the supporting force of the support spring (23) on the vehicle is less than the target supporting force value, the smaller the tensile normal stiffness value of the shock absorber within this stroke range, the smaller the tensile damping, and the better the effect.

[0083] Within all stroke ranges where the supporting force of the support spring (23) on the vehicle exceeds the target supporting force value, the smaller the compression stiffness value of the shock absorber within this stroke range, the smaller the compression damping, and the better the effect.

[0084] When there is both tensile negative stiffness and compressive negative stiffness, and the values ​​of tensile negative stiffness and compressive negative stiffness are different, the absolute value between the values ​​of tensile negative stiffness and compressive negative stiffness is selected as the matching value of the stiffness value of the equivalent support spring (23), and the vibration damper effect is better.

[0085] The purpose of matching the above stiffness values ​​is to make the resultant force of the support spring (23) and the damper equal to or close to the target support force value, so as to achieve the best vibration reduction effect.

[0086] 2. Force matching method

[0087] During the stretching process of the shock absorber, with F 拉实 equal to or close to F 目 To achieve the optimal matching standard between the shock absorber and the support spring (23), during the compression process of the shock absorber, F 压实 equal to or close to F 目 The optimal matching standard between the damper and the support spring (23) is used to achieve the best damping effect.

[0088] The equivalent support spring (23) refers to:

[0089] The spring that provides actual support to the vehicle is converted into an equivalent spring coaxial with the shock absorber. This equivalent spring has the same effect on the vehicle as the original spring.

[0090] Target support force value (F) 目 )refer to:

[0091] The actual weight of the vehicle body acting on the equivalent support spring (23) is taken as the target support force value;

[0092] Alternatively, the target support force value can be the resultant force of the wind resistance force applied to the vehicle body at a certain speed and the vehicle body weight acting on the corresponding equivalent support spring (23).

[0093] Alternatively, the actual force value under its working conditions can be used as the target support force value, that is, the actual force value of the road slope, wind speed, vehicle speed, load, etc., applied to the equivalent support spring (23) can be used as the target force value.

[0094] The stiffness value of the equivalent support spring (23) refers to:

[0095] The stiffness of the support spring (23) that provides actual support to the vehicle is converted into the stiffness value of the equivalent support spring (23) coaxial with the shock absorber.

[0096] Unless otherwise specified, the stiffness of the support spring (23) mentioned in the text refers to the stiffness of the support spring (23) converted into the equivalent stiffness of the support spring (23) coaxial with the shock absorber.

[0097] Scheme E: As described in any of the aforementioned schemes A to D, the one-way valve on the piston is mainly composed of a valve block (7). The valve block (7) and the cylinder wall of the damper cylinder (14) form a sealing surface. There is a liquid inlet channel (11) between the valve block (7) and the piston (6) that communicates with the rod chamber (4) and the rodless chamber (12). The valve block (7) and the piston (6) can move relative to each other, so that the liquid inlet channel (11) is opened or closed when the damper is compressed or stretched. That is, when the damper is compressed, the liquid inlet channel (11) is opened to connect the rodless chamber (12) and the rod chamber (4) of the cylinder. When the damper is stretched, the liquid inlet channel (11) is closed, so the rodless chamber (12) and the rod chamber (4) of the cylinder are not connected. When the liquid inlet channel (11) is closed, the stretching valve (9) forms a damping channel (10) between the rod chamber (4) and the rodless chamber (12). The piston (15) or piston rod (3) has a structure or device that limits the displacement of the valve block (7) to limit the relative displacement between the valve block (7) and the piston.

[0098] Working principle:

[0099] As shown in Figure 1, when the damper is compressed, the piston (6) moves downward until the limiting structure or limiting device contacts the valve block (7) and drives the valve block (7) to move downward together, creating a gap between the valve block (7) and the piston. The rodless chamber and the rod chamber form a connected inlet channel (11), through which the liquid flows into the rod chamber (4). When the damper is stretched, the piston moves upward until the valve block (7) contacts the sealing surface of the piston (6) and drives the valve block (7) to move upward together. A sealing structure is formed between the piston (6) and the valve block (7), preventing the liquid from passing through the sealing surface between the piston (6) and the valve block (7). The liquid flow in the rod chamber (4) flows through the stretching damping valve from the damping channel (10) to the rodless chamber (12).

[0100] Valve block: refers to a device that forms a sealing surface with the cylinder wall and can generate mutual displacement with the piston, and can form an openable and closable channel with the piston or piston rod. It can be composed of a single valve block ring, or it can be composed of auxiliary components such as sealing rings and sealing rings (8) installed on the valve block. The valve block can be a full circular ring or a semi-circular ring, and its structure and composition are not limited.

[0101] Limiting device: Used to limit the displacement between the valve block (7) and the piston. The structure of the limiting device is not limited. The limiting device can be a nut, a retaining ring, a pin, etc., or it can be a limiting structure set on the piston.

[0102] Option F: A vehicle characterized by using any one of the aforementioned options A to E.

[0103] Beneficial effects

[0104] 1. Ensure that the shock absorber has its own optimal resistance value for both its extension and compression strokes, so that the shock absorber can achieve the best vibration reduction effect.

[0105] 2. The damping force of the shock absorber will automatically adjust its resistance value based on the road surface feedback and the supporting force on the vehicle during vehicle operation.

[0106] 3. When the shock absorber is compressed rapidly, the one-way valve on the piston has a larger diameter and less damping, which effectively reduces or avoids the cavitation effect caused by insufficient fluid supply to the shock absorber.

[0107] 4. The problem of quantifying the performance of vibration dampers has been solved, and the performance evaluation standards for vibration dampers have been clarified.

[0108] 5. The problem of performance matching standards between shock absorbers and vehicle support springs has been solved, enabling quantitative performance standards for the matching of shock absorbers and vehicle support springs.

[0109] 6. It can effectively avoid the influence of temperature on the performance of the shock absorber, so that the performance of the shock absorber is basically unaffected by the temperature of the oil inside the shock absorber.

[0110] 7. This invention corrects the long-standing bias that the damping force of a shock absorber should be related to speed. The damping force of the shock absorber in this invention is only related to the stroke of the shock absorber and the force of the supporting spring, so that the damping force of the shock absorber is basically unaffected by the tensile and compressive speeds. Attached Figure Description

[0111] Figure 1: Partial cross-sectional view of a tension-damped controlled vibration damper

[0112] Figure 2: Schematic diagram of the stroke position of the tension-damped controlled vibration damper

[0113] Figure 3: Schematic diagram of a dual-controlled vibration damper with tensile and compressive damping (compression damping controlled position)

[0114] Figure 4: Schematic diagram of a dual-controlled vibration damper with tensile and compressive damping (controlled position for tensile damping)

[0115] Figure 5: Schematic diagram of the stroke position of a dual-controlled damper with tensile and compressive damping.

[0116] Figure 6: 3D schematic diagram of the bottom valve seat

[0117] Figure 7: 3D schematic diagram of piston and valve block

[0118] Figure 8: Correspondence between damper stroke and various force values

[0119] Figure 9: Schematic diagram showing the relationship between the shock absorber stroke and various force values.

[0120] (The central axes of the damper and the support spring in Figure 9 are not coaxial. This is only for the convenience of showing the spring, the damper and their resultant force relationship in the figure. In actual application, the stress relationship between the damper and the support spring should be calculated in an equivalent coaxial manner.)

[0121] Illustration Number and Name:

[0122] 1-Reservoir cylinder 2-Reservoir chamber 3-Piston rod 4-Rod chamber 5-Guide belt 6-Piston 7-Valve block

[0123] 8-Sealing ring; 9-Tension valve; 10-Tension damping channel; 11-Compression inlet channel; 12-Rodless chamber (compression chamber)

[0124] 13-Spring 14-Cylinder (Hydraulic Cylinder) 15-Snap Ring 16-Spring Plate 17-Check Valve Plate 18-Bottom Valve Seat

[0125] 19-Compression valve 20-Compression damping channel 21-Tension inlet channel 22-Shock absorber 23-Support spring The best embodiment of the present invention

[0126] The preferred embodiment of the present invention is preferred embodiment 3 (as shown in Figures 3, 4, and 5). Embodiments of the present invention

[0127] Preferred option 1 (Figure 1, Figure 2):

[0128] A tension-damped controlled vibration damper includes: a cylinder (14), a piston rod (3), and a piston (6); the piston (6) has a one-way valve and a valve hole that cooperates with the valve core of the tension valve. The valve hole communicates with the rod chamber. The valve core of the tension valve (9) is placed in the rodless chamber (12). A spring (13) is provided between the valve core and the bottom of the inner cylinder (14) or the bottom valve. When the valve core of the tension valve (9) and the valve hole are subjected to the force of the spring (13), a tension damping valve is formed. When the vibration damper is stretched, it is subjected to the action of the damping valve to achieve the vibration reduction effect. That is, at any position within the spring compression stroke during the stretching stroke of the vibration damper, the stretching damping force of the vibration damper is proportional to the compressive force on the spring.

[0129] 0129. Working principle:

[0130] 0130. As shown in Figure 1, the valve core of the tension valve (9) is subjected to the force of the spring (13) and cooperates with the valve hole to form a tension damping valve. During the process of the piston (6) moving from L1 to L2, the spring (13) transitions from a compressed state to a free state. The fluid flows from the rodless chamber (12) through the tension damping channel (10) into the rod chamber (4). The damping of the tension valve (9) decreases from large to small, that is, the tension damping force of the shock absorber decreases from large to small. When the piston moves up to L2 (the free length position of the spring), the tension valve (9) is in the open position, and the damping reaches the minimum value until the piston moves up to L3. During the process of the piston moving down from L3 to L2, the spring (13) is in the free state, the tension valve (9) is in the open position, and the fluid flows from the rod chamber (4) through the compression damping channel (11) and the tension damping channel (10) into the rodless chamber. During the process of the piston moving down from L2 to L1, the spring (13) is in a compressed state, the tension valve (9) is in the closed position, and the fluid flows from the rod chamber (4) through the compression damping channel (11) into the rodless chamber (12), that is, through the check valve (7) into the rodless chamber (12).

[0131] The performance of a vibration damper can be expressed in the following ways:

[0132] The tensile damping stiffness value for the stretching strokes L1~L2 is -nkgf / cm.

[0133] The compression damping stiffness values ​​for the compression strokes L1~L2 are nkgf / cm.

[0134] In -nkgf / cm, n represents the actual numerical value. For example, -5kgf / cm means that for every 1 cm increase in the stretching stroke of L1~L2 in the stretching direction, the stretching damping is reduced by 5 kg of stretching force.

[0135] Other performance representation methods can also be used. Any method that can represent the stiffness performance of the vibration damper and the relationship between each stiffness and position is considered an equivalent representation method.

[0136] Matching scheme between the shock absorber and the support spring (23):

[0137] Within all stroke ranges where the supporting force of the support spring (23) on the vehicle exceeds the target supporting force value, the closer the absolute value of the shock absorber's tensile stiffness is to the stiffness value of the equivalent support spring (23), the better the damping effect. That is, the selection criterion is that the stiffness of the equivalent support spring (23) is equal to or close to the absolute value of the shock absorber's tensile stiffness. Furthermore, when the vehicle is traveling at a constant speed in a straight line on a flat road, the closer the stretching or compression position of the shock absorber is to L2, the better the effect of the shock absorber (limited to the stretching or compression position of the shock absorber after initial installation). That is, when the actual force of the support spring (23) is equal to the target supporting force value, the closer the stretching or compression position of the shock absorber is to L2, the better the damping effect.

[0138] When a vehicle is traveling at a constant speed and load on a flat road surface, the closer the stretching or compression position of the shock absorber is to L2, and the closer the absolute value of the stretching stiffness of the shock absorber in L1~L2 is to the stiffness value of the equivalent support spring (23), the better the shock absorber's damping effect is when it matches the vehicle at this speed.

[0139] 0139. For example: When a vehicle is traveling at a speed of 60 km / h, with a load of 200 kg, and is moving horizontally and straight at a constant speed, the equivalent support force of the front left support spring (23) is 500 kgf, and the stiffness of the support spring (23) is 25 kgf / cm. Then, the closer the front left shock absorber matched with the vehicle is to L2 when the spring support force is 500 kgf, and the closer the absolute value of the shock absorber's tensile stiffness is to 25 kgf / cm within the stroke of L1~L2, the better the shock absorption effect. Similarly, shock absorbers in other positions can be matched to achieve the best effect.

[0140] L2 can also be understood as the critical point of force balance of the spring. That is, the L2 point of the shock absorber is the force balance point when the vehicle is traveling horizontally at a constant speed under a specified load. L1~L2 is the case of excessive support force, and L2~L3 (Figure 2) is the case of insufficient support force. When matching shock absorbers, the closer L2 is to or the closer it is to this force balance point, and the closer the absolute value of the tensile stiffness of the shock absorber in the L1~L2 stroke is to the stiffness of the supporting spring, the better the damping effect.

[0141] Preferred Option 2:

[0142] A compression-damped controlled vibration damper includes: a cylinder, a piston rod, a piston, and a bottom valve. The bottom valve is equipped with a compression valve and a check valve. The check valve on the bottom valve consists of a check valve plate (17) and a spring plate (16). The valve core of the compression valve is connected to the piston or piston rod via a spring, so that the damping force of the compression valve is controlled by the piston stroke and the spring tension. When the vibration damper is compressed and the spring is stretched, the damping valve acts as a damping valve. The greater the spring tension, the greater the compression damping, thereby achieving the vibration reduction effect. The compression damping force at any position within the spring tension range during the compression stroke of the vibration damper is proportional to the spring tension. At any position within the spring compression range during the compression stroke of the vibration damper, the compression damping force of the vibration damper is approximately the compression force when the spring is compressed.

[0143] Working principle:

[0144] As shown in Figure 3: The valve core (19) of the compression valve is pulled by the spring (13) and cooperates with the valve orifice of the compression valve to form a damping valve. During the process of the piston moving down from position L4 to position L3, the spring (13) transitions from a stretched state to a free state, and the damping force of the damping valve decreases from large to small, that is, the compression damping force of the shock absorber decreases from large to small. The fluid flows from the rodless chamber through the compression damping channel (20) to the reservoir chamber. When the piston moves down to position L3 (the free length position of the spring), the compression damping reaches the minimum value until the piston moves down to position L1. When the piston moves down from position L2 to position L1, the spring is compressed, the valve core of the compression valve is located at the bottom valve, and the compression valve is in the fully open state. When the shock absorber is compressed, the fluid flows from the rodless chamber through the compression damping channel (20) to the reservoir chamber (2).

[0145] Methods for representing the performance of vibration dampers:

[0146] The tensile damping stiffness values ​​for the stretching strokes L1~L2 and L3~L4 are nkgf / cm.

[0147] The compression damping stiffness value for the compression strokes L4 to L3 is -nkgf / cm.

[0148] The stiffness values ​​of L2 to L3 are approximately nkgf / cm.

[0149] Spring matching method:

[0150] Within all stroke ranges where the support force of the support spring (23) on the vehicle is less than the target support force value, the better the damping effect is, the closer the absolute value of the compressive stiffness of the shock absorber is to the stiffness value of the equivalent support spring (23). That is, the selection criterion is that the stiffness of the equivalent support spring (23) is equal to or close to the absolute value of the shock absorber stiffness. When the support force of the support spring (23) on the vehicle is equal to the target support force value, the tension and compression position of the shock absorber should be set between L2 and L3.

[0151] That is, when the vehicle is traveling at a constant speed on a flat road, the tension or compression position of the shock absorber should be set between L2 and L3, and the closer the absolute value of the compression stiffness of the shock absorber in L3 to L4 is to the stiffness value of the equivalent support spring (23), the better the damping effect.

[0152] Preferred option 3 (Figures 3, 4, and 5):

[0153] A dual-controlled damper with tension and compression damping includes: a cylinder, a piston rod, a piston, and a bottom valve. The piston is equipped with a tension valve and a check valve, and the bottom valve is equipped with a compression valve and a check valve. The check valve on the bottom valve includes a check valve plate (17) and a spring plate (16). The valve core of the compression valve is connected to the valve core of the tension valve via a spring. A limiting device for the valve core of the tension valve is provided on the piston or piston rod to limit the displacement of the tension valve, so that the damping force values ​​of both the compression valve and the tension valve are controlled by the piston stroke and the spring tension force. When the damper is stretched or compressed, the tension damping force value or the compression damping force value changes with the piston stroke to achieve the damping effect. Specifically, at any position within the spring compression stroke of the damper's stretch stroke, the tension damping force value of the damper is proportional to the compression force on the spring; at any position within the spring tension stroke of the damper's compression stroke, the compression damping force value is proportional to the tension force on the spring.

[0154] Working principle:

[0155] As shown in Figure 3:

[0156] When the piston compresses downwards, the valve core (19) of the compression valve is pulled by the spring (13) and cooperates with the valve orifice of the compression valve to form a damping valve. During the process of the piston moving down from position L4 to position L3, the spring (13) transitions from a stressed state to a free state, and the damping force of the damping valve decreases, that is, the compression damping force of the shock absorber decreases. When the piston moves down to position L3 (the free length position of the spring), the damping reaches its minimum value until the piston moves down to position L1. When the piston moves down from position L2 to position L1, the spring is compressed, the valve core of the compression valve is located at the bottom of the valve, and the compression valve is in the fully open state.

[0157] As the piston is pulled upwards, the valve core of the tension valve, under the action of the spring force, engages with the valve orifice to form a damping valve. During the process of the piston moving upwards from L1 to L2, the spring transitions from a compressed state to a free state, and the damping of the damping valve decreases, that is, the tension damping force of the shock absorber decreases. When the piston moves upwards to the L2 position (the free length position of the spring), the damping reaches its minimum value, until the piston moves upwards to the L4 position.

[0158] When the piston moves downward, the liquid flows from the rodless chamber through the compression inlet channel (11) to the rod chamber, while the liquid in the rodless chamber enters the reservoir through the compression damping channel (20).

[0159] When the piston moves upward, the liquid flows from the reservoir (2) into the rodless chamber (12) through the tension inlet channel (21), while the liquid in the rod chamber (4) flows into the rodless chamber (12) through the tension damping channel (10).

[0160] Methods for representing the performance of vibration dampers:

[0161] The tensile damping stiffness value for the stretching strokes L1~L2 is -nkgf / cm.

[0162] The compression damping stiffness values ​​for the compression strokes L1~L2 are nkgf / cm.

[0163] The tensile damping stiffness value for the stretching strokes L3 to L4 is n kgf / cm.

[0164] The compression damping stiffness value for the compression strokes L3 to L4 is -nkgf / cm.

[0165] The tensile and compressive stiffness values ​​of L2~L3 are approximately nkgf / cm.

[0166] n represents the actual numerical value at each position in the row.

[0167] Stiffness value matching method:

[0168] Within all strokes (L3~L4 stroke positions) where the support force of the support spring (23) on the vehicle is less than the target support force value, the better the damping effect is, the closer the absolute value of the compressive stiffness of the damper is to the stiffness value of the equivalent support spring (23) within this stroke range.

[0169] Within all strokes (L1~L2 stroke positions) where the support force of the support spring (23) on the vehicle is greater than the target support force value, the better the damping effect is, the closer the absolute value of the tensile stiffness of the damper within this stroke range is to the stiffness value of the equivalent support spring (23).

[0170] When the support force of the support spring (23) on the vehicle is near the target support force value (L2~L3 stroke position), the smaller the absolute values ​​of the compression stiffness, tension stiffness and damping value of the shock absorber, the better.

[0171] Force matching method:

[0172] During the shock absorber's tensioning process, with F 拉实 equal to or close to F 目 As the optimal matching standard between the damper and the support spring (23), during the compression process of the damper, with F 压实 equal to or close to F 目 As the best matching standard for shock absorbers and support springs (23).

[0173] That is, within all strokes (L3~L4 stroke positions) where the support force of the support spring (23) on the vehicle is less than the target support force value, the shock absorber is in a stretched state, and the minimum tensile damping force value is used as the matching standard, so that F 拉实 Try to get as close to F as possible 目 When the shock absorber is in a compressed state, it uses F 压实 Try to equal F 目 As a standard for matching compression damping force values;

[0174] Similarly, within all travel ranges (L1~L2 travel positions) where the support force of the support spring (23) on the vehicle is greater than the target support force value, the shock absorber is in a stretched state and uses F 拉实 Try to equal F 目 As a matching standard for tensile damping, when the shock absorber is in compression, the minimum compressive damping force is used as the matching standard, so that F 压实 Try to get as close to F as possible 目。

[0175] Preferred option 4 (Figure 1, Figure 3):

[0176] The vibration dampers described in the aforementioned preferred embodiments are characterized in that: the one-way valve on the piston includes a valve block (7). The valve block (7) and the cylinder wall of the hydraulic cylinder of the vibration damper form a sealing surface, and the valve block (7) and the piston form a channel connecting the rodless chamber and the rod chamber. The valve block (7) and the piston move relative to each other to form an open or closed channel. When the channel is open, it connects the rodless chamber and the rod chamber of the cylinder; when the channel is closed, the rodless chamber and the rod chamber of the cylinder are not connected. The piston or piston rod has a structure or device that limits the displacement of the valve block (7), thereby limiting the relative displacement between the valve block (7) and the piston.

[0177] Working principle:

[0178] As shown in Figure 1, when the damper is compressed, the piston (6) moves downward until the limiting structure or limiting device contacts the valve block (7) and drives the valve block (7) to move downward together, creating a gap between the valve block (7) and the piston (6). The rodless chamber (12) and the rod chamber (4) form a connected liquid inlet channel (11), and the liquid flows from the rodless chamber (12) into the rod chamber (4) through the compression liquid inlet channel (11). When the damper is stretched, the piston (6) moves upward until the valve block (7) contacts the sealing surface of the piston (6) and drives the valve block (7) to move upward together. A sealing structure is formed between the piston (6) and the valve block (7), and the liquid cannot pass through the sealing surface between the piston (6) and the valve block (7). The liquid flow in the rod chamber (4) can only flow to the rodless chamber (12) through the stretching valve.

[0179] Preferred Option 5:

[0180] A vehicle that uses any one of the shock absorbers described in preferred schemes 1-4. Industrial applicability

[0181] The shock absorber of the present invention is applicable to all vehicles, and the shock absorber can be designed, manufactured and used in accordance with the present invention.

Claims

1. A vibration damper, comprising: The cylinder (14), piston rod (3), piston (6), check valve, tension valve or compression valve, characterized in that: a spring (13) is provided in the rodless chamber (12) of the cylinder of the shock absorber, and the end of the spring is connected to a tension valve (9) or compression valve (19). When the shock absorber is stretched or compressed, the change in distance between the piston (6) and the bottom of the cylinder (14) controls the change in the stretching amount or compression amount of the spring (13), thereby controlling the damping force value of the tension valve (9) or compression valve (19) of the shock absorber. When the shock absorber is in a state of tension and the spring is compressed, it has a negative stiffness tensile damping coefficient. When the damper is in a state of compression and the spring is under tension, it has a negative stiffness compression damping coefficient.

2. The vibration damper as described in claim 1; characterized in that: The piston (6) is equipped with a check valve and a valve hole that cooperates with the valve core of the tension valve (9). The valve hole is connected to the rod chamber (14). The valve core of the tension valve (9) is placed in the rodless chamber (12). A spring (13) is provided between the valve core of the tension valve (9) and the bottom of the cylinder or the bottom valve. During the tensioning process of the damper, when the spring (13) is under pressure, the valve core of the tension valve (9) and the valve hole are subjected to the compression force of the spring (13) to form a tension damping valve.

3. The vibration damper as described in claim 1; characterized in that... The bottom valve (18) is equipped with a compression valve (19) and a check valve (16, 17). The valve core of the compression valve (19) is connected to the piston (6), plunger or piston rod (3) through a spring. During the compression process of the damper, when the spring (13) is in a tensile state, the damping force of the compression valve (19) is controlled by the stroke of the piston (6) and the tension of the spring (13).

4. The vibration damper as described in claim 1; characterized in that... The piston (6) is equipped with a tension valve (9) and a check valve, and the bottom valve (18) is equipped with a compression valve (19) and a check valve (16, 17). The valve core of the tension valve (9) is connected to the valve core of the compression valve (19) through a spring (13). The piston (6) or piston rod (3) is equipped with a limiting device to restrict the stroke of the valve core of the tension valve (9). During the compression process of the shock absorber, when the spring (13) is in a tension state, the damping force of the compression valve (19) is controlled by the stroke of the piston (6) and the tension force of the spring (13). During the tension process of the shock absorber, when the spring (13) is in a compression state, the damping force of the tension valve (9) is controlled by the stroke of the piston (6) and the compression force of the spring (13).

5. The vibration damper as described in claims 1-4, characterized in that: The one-way valve on the piston (6) is mainly composed of a valve block (7). The valve block (7) and the cylinder wall of the shock absorber cylinder (14) form a sealing surface. There is an inlet channel (11) between the valve block (7) and the piston (6) that communicates with the rod chamber (4) and the rodless chamber (12). The valve block (7) and the piston (6) can move relative to each other, so that the inlet channel (11) is opened or closed when the shock absorber is compressed or stretched.

6. The method for representing the performance of the vibration damper as described in claims 1-4: the damping performance of the vibration damper is represented by the stiffness value corresponding to each stroke position of the vibration damper's tension stroke and compression stroke, or by the stroke position corresponding to each stiffness value.

7. A vehicle characterized by: The vibration damper described in any of claims 1-4 was used.

8. The method of matching the force value of the damper (22) and the support spring (23) as described in claims 1-4: during the tensioning process of the damper (22), with force value F 拉实 equal to or close to F 目 As a standard for matching the damper (22) with the support spring (23); during the compression of the damper (22), with F 压实 equal to or close to F 目 As a standard for matching the shock absorber (22) with the support spring (23).

9. The damper (22) and the support spring (23) as described in claims 1-4 are matched using a stiffness matching method: Within all stroke ranges where the support force of the support spring (23) on the vehicle is less than the target support force value, the better the damping effect is, the closer the absolute value of the compression stiffness of the damper (22) within this stroke range is to the stiffness value of the equivalent support spring (23). Within all stroke ranges where the supporting force of the support spring (23) on the vehicle exceeds the target supporting force value, the closer the absolute value of the tensile stiffness of the damper (22) within this stroke range is to the stiffness value of the equivalent support spring (23), the better the damping effect. When the supporting force of the supporting spring (23) on the vehicle is equal to the target supporting force value, the damping force value of the shock absorber should be as small as possible.

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