A suspension decoupling membrane structure with reduced dynamic stiffness

Abstract

This utility model discloses a suspension decoupling membrane structure for reducing dynamic stiffness, relating to the field of automotive suspension technology. The device includes a diaphragm body located within a flow channel decoupling membrane groove. The diaphragm body has several first buffer ribs evenly distributed along its length on its upper and lower surfaces. Between adjacent first buffer ribs, several second buffer ribs are evenly distributed along their width on the diaphragm body, with the length direction of the second buffer ribs perpendicular to that of the first buffer ribs. The sides of the first and second buffer ribs away from the diaphragm body respectively abut against the top cover plate and the bottom of the flow channel decoupling membrane groove. This utility model enables the suspension decoupling membrane to maintain low dynamic stiffness not only under high-frequency micro-amplitude vibrations but also to provide a large damping angle under low-frequency large-amplitude vibrations, thereby effectively suppressing abnormal noises and improving in-vehicle quietness.

Description

Technical Field

[0001] This invention belongs to the field of automotive mounting technology, specifically a mounting decoupling membrane structure for reducing dynamic stiffness. Background Technology

[0002] As the automotive industry continues its rapid development towards high performance, the evolution of automotive technology, while pursuing excellent economic efficiency, also places increasingly stringent demands on driving comfort, safety, and ride quality. In the field of vehicle NVH (noise, vibration, and harshness) performance optimization, the suspension system, as a key elastic support component connecting the powertrain (engine and transmission) to the vehicle body, directly affects the vehicle's vibration reduction and noise reduction effects, ride comfort, and driving stability. Hydraulic suspensions, combining the elasticity of the rubber spring with the hydraulic damping effect of the internal fluid chamber, exhibit significant advantages in effectively isolating low-frequency, large-amplitude vibrations in the powertrain and attenuating impact loads, making them a mainstream solution for improving overall vehicle comfort. The hydraulic suspension decoupling diaphragm, as one of its core components, plays a crucial role in optimizing the vibration transmission path. Its structural design directly determines the fluid flow characteristics and pressure balance capability of the fluid chamber under dynamic conditions, which is essential for reducing system mechanical noise, broadening the effective vibration isolation frequency band, and improving high-frequency NVH performance. Therefore, decoupling diaphragms need to have excellent vibration and shock buffering capabilities, the ability to suppress flow noise (abnormal noise), and provide a sufficiently large damping phase angle (damping angle) to meet the needs of fine-tuning the dynamic characteristics of the suspension under complex working conditions.

[0003] However, existing hydraulic suspension decoupling diaphragm structures still have significant shortcomings in meeting the above requirements, especially in pursuing lower dynamic stiffness. Under high-frequency micro-amplitude vibration excitation, the stiffness characteristics of the traditional decoupling diaphragm structure often become a limiting factor. On the one hand, to withstand the pressure difference in the fluid cavity and ensure structural strength, the diaphragm needs to maintain a certain overall stiffness, which leads to a higher dynamic stiffness value in the high-frequency domain, weakening the isolation effect of the hydraulic suspension on high-frequency vibrations and affecting the quietness of the vehicle interior. On the other hand, existing diaphragm designs often present a contradiction between optimizing fluid flow to provide an ideal damping angle and reducing high-frequency dynamic stiffness: thin or flexible structures pursuing low dynamic stiffness may sacrifice low-frequency damping effects and structural durability, and are prone to inducing fluid turbulence or cavitation during dynamic deformation, producing abnormal flow noises (such as "gurgling" sounds); while complex structures designed to enhance damping and suppress abnormal noises (such as labyrinth channels or porous designs) may introduce additional local stiffness, which is not conducive to reducing overall dynamic stiffness. Therefore, there is an urgent need to develop a new type of decoupling diaphragm structure that can effectively ensure low-frequency damping performance and suppress abnormal noise while significantly reducing the dynamic stiffness of the system under high-frequency micro-amplitude vibration, thereby comprehensively improving the broadband vibration isolation performance of hydraulic suspension. Utility Model Content

[0004] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes a suspension decoupling membrane structure that reduces dynamic stiffness, resolving the contradiction between providing an ideal damping angle and reducing high-frequency dynamic stiffness in existing suspension decoupling membranes.

[0005] To achieve the above objectives, according to an embodiment of the first aspect of this utility model, a suspended decoupling membrane structure for reducing dynamic stiffness is proposed. The suspended decoupling membrane structure includes a membrane body located within a flow channel decoupling membrane groove. The upper and lower surfaces of the membrane body are respectively provided with a plurality of first buffer ribs evenly distributed along the length direction. Between two adjacent first buffer ribs, a plurality of second buffer ribs are provided along the membrane body evenly distributed along the width direction. The length direction of the second buffer ribs is perpendicular to the length direction of the first buffer ribs. The sides of the first and second buffer ribs away from the membrane body abut against the top cover plate of the flow channel decoupling membrane groove and the bottom of the flow channel decoupling membrane groove, respectively.

[0006] As a further technical solution of this utility model, the diaphragm body includes a semi-circular portion and a rectangular portion, the two semi-circular portions are respectively disposed at both ends of the rectangular portion, and the semi-circular portion and the rectangular portion are integrally formed.

[0007] As a further technical solution of this utility model, the first buffer rib and the second buffer rib have the same structure, and both the first buffer rib and the second buffer rib are composed of an abutting part, a transition part and a supporting part. The supporting part is connected to the diaphragm body, the transition part is located on the side of the supporting part away from the diaphragm body, and the abutting part is located on the side of the transition part away from the supporting part. The abutting part, the transition part and the supporting part are integrally formed.

[0008] As a further technical solution of this utility model, the abutting part includes a strip-shaped protrusion and an end protrusion. The strip-shaped protrusion has a semi-cylindrical structure, and the end protrusion has a quarter-sphere structure. The two end protrusions are disposed at both ends of the strip-shaped protrusion. The abutting part and the opposing side of the supporting part are equal, and the cross-section of the transition part is the same.

[0009] As a further technical solution of this utility model, the cross-section of the support gradually decreases from the direction away from the diaphragm body, and the side of the support is configured as a curved surface structure that gradually expands towards the diaphragm body.

[0010] As a further technical solution of this utility model, the suspended decoupling membrane structure also includes a sealing ring, which is distributed circumferentially along the edge of the membrane body, and the height of the sealing ring is flush with the depth of the flow channel decoupling membrane groove.

[0011] As a further technical solution of this utility model, the cross-sectional radii of the strip-shaped protrusion and the end protrusion are equal.

[0012] As a further technical solution of this utility model, the first buffer ribs on the upper and lower surfaces of the diaphragm body respectively abut against the first transverse rib of the cover plate and the second transverse rib at the bottom of the flow channel decoupling membrane groove.

[0013] As a further technical solution of this utility model, the second buffer ribs on the upper and lower surfaces of the diaphragm body respectively abut against the first longitudinal rib of the cover plate and the second longitudinal rib at the bottom of the flow channel decoupling membrane groove.

[0014] As a further technical solution of this utility model, there are no fewer than three second buffer ribs between two adjacent first buffer ribs, and the number of second buffer ribs is odd.

[0015] Compared with the prior art, the beneficial effects of this utility model are:

[0016] 1. In this invention, a multi-point elastic support and distributed flexible deformation zone is formed by setting a network of first and second buffer ribs that are perpendicular to each other and evenly distributed on the upper and lower surfaces of the diaphragm body. Under high-frequency micro-amplitude vibration conditions, these densely distributed buffer ribs can effectively absorb and dissipate energy through their own elastic deformation, greatly weakening the rigid path through which the diaphragm body transmits vibration. Compared with traditional flat diaphragms of single thickness or simple curved diaphragms, this structure significantly reduces the overall dynamic stiffness of the diaphragm in the high-frequency domain, thereby greatly improving the isolation efficiency of the hydraulic suspension for key high-frequency vibrations and effectively improving the quietness of the vehicle interior.

[0017] 2. In this invention, the first and second buffer ribs abut against the bottom of the cover plate and the decoupling membrane groove of the flow channel, respectively, facilitating buffering under low-frequency, large-amplitude vibrations or impact loads. The mutually perpendicular layout of the buffer ribs optimizes the fluid flow pattern within the liquid cavity, effectively suppressing fluid turbulence and cavitation, and significantly reducing the risk of abnormal flow noises (such as "gurgling" sounds). Simultaneously, the evenly distributed buffer ribs ensure balanced pressure transmission throughout the entire diaphragm area, avoiding localized stress concentration and abnormal deformation. While ensuring structural durability, it provides the necessary large damping angle to attenuate low-frequency, large-amplitude vibrations. Attached Figure Description

[0018] Figure 1 This is a cross-sectional view of the suspension decoupling membrane structure of this utility model installed in a hydraulic suspension;

[0019] Figure 2 This is a perspective view of a suspension decoupling membrane structure for reducing dynamic stiffness according to the present invention.

[0020] Figure 3 This is a top view of a suspension decoupling membrane structure for reducing dynamic stiffness according to the present invention.

[0021] Figure 4 for Figure 3 Sectional view along the middle AA direction;

[0022] Figure 5 This is a perspective view of the first buffer rib in a suspension decoupling membrane structure for reducing dynamic stiffness according to this utility model.

[0023] Figure 6 This is a cross-sectional view of the hydraulic suspension after the decoupling membrane structure of the suspension has been removed.

[0024] In the figure: 100, flow channel decoupling membrane groove; 101, second transverse rib; 102, second longitudinal rib; 200, diaphragm body; 201, semi-circular part; 202, rectangular part; 300, first buffer rib; 301, abutment part; 3011, strip-shaped protrusion; 3012, end protrusion; 302, transition part; 303, support part; 400, second buffer rib; 500, cover plate; 501, first transverse rib; 502, first longitudinal rib; 600, sealing ring. Detailed Implementation

[0025] The technical solution of this utility model will be clearly and completely described below with reference to the embodiments. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.

[0026] like Figures 1-6 As shown, a suspended decoupling membrane structure for reducing dynamic stiffness includes a membrane body 200 located within a flow channel decoupling membrane groove 100. The upper and lower surfaces of the membrane body 200 are respectively provided with a plurality of first buffer ribs 300 evenly distributed along their length direction. Between two adjacent first buffer ribs 300, a plurality of second buffer ribs 400 are provided along the membrane body 200 and evenly distributed along their width direction. The length direction of the second buffer ribs 400 is perpendicular to the length direction of the first buffer ribs 300. The sides of the first buffer ribs 300 and the second buffer ribs 400 away from the membrane body 200 respectively abut against the top cover plate 500 and the bottom of the flow channel decoupling membrane groove 100.

[0027] It should be noted that the core of the diaphragm body 200 consists of a network of first and second buffer ribs 300 and 400 arranged uniformly and perpendicularly on the upper and lower surfaces. Under high-frequency micro-amplitude vibration, these ribs mainly rely on their own elastic bending and compression / tension deformation to absorb and dissipate energy, significantly weakening the rigid path of vibration transmission, thereby effectively reducing the dynamic stiffness of the system in the high-frequency range and improving the vibration isolation effect and vehicle interior quietness. When faced with low-frequency large-amplitude vibration or impact load, the end of the rib away from the diaphragm body 200 will contact and compress with the cover plate 500 and the bottom of the flow channel decoupling membrane groove 100, providing a controllable nonlinear hydraulic damping path and enhancing the attenuation capability for low-frequency large vibration (providing the required large damping angle). At the same time, this regular, vertically interlaced rib layout guides and optimizes the fluid flow pattern in the liquid cavity, effectively suppressing the generation of turbulence and cavitation, and significantly reducing the risk of abnormal fluid flow noise. This achieves synergistic optimization of high-frequency low dynamic stiffness and low-frequency high damping / low noise under different operating conditions, overcoming the contradictions in traditional design and comprehensively improving the wide-range NVH performance of the suspension.

[0028] like Figures 2-3 As shown, the diaphragm body 200 includes a semi-circular portion 201 and a rectangular portion 202. The two semi-circular portions 201 are respectively disposed at both ends of the rectangular portion 202, and the semi-circular portions 201 and the rectangular portion 202 are integrally formed.

[0029] It should be noted that the rectangular part 202 provides a stable main support area, while the two semi-circular parts 201 on both sides perfectly match the typical contour of the hydraulic suspension fluid chamber; at the same time, the semi-circular design eliminates the rigid abrupt change point in the right-angle area of ​​the traditional rectangular diaphragm, making the fluid flow smoother and further suppressing turbulent noise. The overall structure optimizes space utilization and system durability while ensuring mechanical strength.

[0030] like Figure 2 and Figure 5 As shown, the first buffer rib 300 and the second buffer rib 400 have the same structure, and both the first buffer rib 300 and the second buffer rib 400 are composed of an abutment portion 301, a transition portion 302 and a support portion 303. The support portion 303 is connected to the diaphragm body 200. The transition portion 302 is located on the side of the support portion 303 away from the diaphragm body 200. The abutment portion 301 is located on the side of the transition portion 302 away from the support portion 303. The abutment portion 301, the transition portion 302 and the support portion 303 are integrally formed.

[0031] It should be noted that the support part 303 ensures a reliable connection and basic strength with the diaphragm body 200, and the transition part 302 achieves smooth stress transfer, significantly reducing the risk of stress concentration and improving fatigue resistance. At the same time, the specific curved surface design of the contact part 301 provides progressive extrusion deformation when contact extrusion occurs, which enhances the low-frequency damping effect and avoids local impact damage. While ensuring high-frequency elastic deformation capability (reducing dynamic stiffness), the overall structure optimizes load distribution and durability through the synergistic effect of each part, and effectively suppresses vibration and abnormal noise.

[0032] like Figure 5 As shown, the abutment portion 301 includes a strip-shaped protrusion 3011 and an end protrusion 3012. The strip-shaped protrusion 3011 has a semi-cylindrical structure, and the end protrusion 3012 has a quarter-spherical structure. The two end protrusions 3012 are disposed at both ends of the strip-shaped protrusion 3011. The abutment portion 301 has the same facing side as the support portion 303 and the same cross-section as the transition portion 302.

[0033] It should be noted that the design combines a semi-cylindrical strip protrusion 3011 with a quarter-spherical end protrusion 3012. The semi-cylindrical part provides continuous and stable longitudinal line contact, ensuring uniform transmission of damping force and reducing local stress. The quarter-spherical end protrusions 3012 at both ends not only completely eliminate stress concentration points at traditional right-angled edges, significantly improving fatigue life, but also achieve a smooth transition at the moment of contact, effectively avoiding impact noise. The overall design takes into account the smoothness of high-frequency elastic contact and the structural reliability under low-frequency high loads, optimizing damping performance and NVH performance.

[0034] like Figure 1 and Figure 5 As shown, the cross-section of the support portion 303 gradually decreases from the direction away from the diaphragm body 200, and the side of the support portion 303 is configured as a curved surface structure that gradually expands towards the diaphragm body 200.

[0035] It should be noted that the support part 303 adopts a curved surface design with an upwardly tapered cross-section and a gradually expanding side. A wide cross-section connection area is formed at the root to ensure a strong bond with the diaphragm body 200 and avoid the risk of delamination. The upwardly tapered structure significantly reduces the stiffness of the rib itself and enhances the high-frequency elastic deformation capability to optimize dynamic stiffness. The gradually expanding curved surface realizes the smooth diffusion of stress, effectively suppresses stress concentration and improves fatigue resistance. At the same time, the special contour increases the effective deformation space and enhances the vibration energy absorption efficiency. Overall, it maximizes the high-frequency vibration isolation effect while ensuring structural reliability.

[0036] like Figures 1-2 As shown, the suspended decoupling membrane structure also includes a sealing ring 600, which is distributed circumferentially along the edge of the membrane body 200, and the height of the sealing ring 600 is flush with the depth of the flow channel decoupling membrane groove 100.

[0037] It should be noted that the design of the sealing ring 600 being fully distributed circumferentially along the edge of the diaphragm body 200 and with its height flush with the depth of the diaphragm groove, forms a full-circumferential, dead-angle-free sealing barrier through pre-compression, completely eliminating the risk of liquid cavity leakage; the precise height matching ensures that the sealing ring 600 and the groove wall of the flow channel decoupling diaphragm groove 100 are uniformly fitted after assembly, eliminating the hidden dangers of local stress concentration or sealing failure caused by traditional height deviation.

[0038] like Figures 4-5 As shown, the cross-sectional radii of the strip protrusion 3011 and the end protrusion 3012 are equal.

[0039] It should be noted that, in this embodiment, the cross-sectional radius of the strip protrusion 3011 and the end protrusion 3012 is specifically 0.5mm. The equal radius design ensures that the curved surfaces of the strip protrusion 3011 and the end protrusion 3012 are perfectly integrated, eliminating geometric abrupt change points to prevent stress concentration and significantly improving fatigue resistance. The consistent radius of curvature ensures a smooth transition when the fluid flows along the ribs, effectively suppressing turbulence and cavitation noise. The seamless connection between the spherical end and the semi-cylinder enhances contact stability and can still provide uniform damping force under off-center loading conditions. The equal radius structure simplifies mold manufacturing and component forming processes, ensures dimensional accuracy and consistency in mass production, and optimizes the elastic deformation coordination under high-frequency vibration.

[0040] like Figures 1-2 and Figure 6 As shown, the first buffer ribs 300 on the upper and lower surfaces of the diaphragm body 200 abut against the first transverse ribs 501 of the cover plate 500 and the second transverse ribs 101 at the bottom of the flow channel decoupling membrane groove 100, respectively.

[0041] It should be noted that precisely constraining the deformation path of the buffer ribs avoids mechanical noise caused by disordered tapping; the directional contact between the ribs and buffer ribs forms distributed energy dissipation nodes, significantly improving the high-frequency vibration isolation efficiency.

[0042] like Figures 1-2 and Figure 6 As shown, the second buffer ribs 400 on the upper and lower surfaces of the diaphragm body 200 abut against the first longitudinal rib 502 of the cover plate 500 and the second longitudinal rib 102 at the bottom of the flow channel decoupling membrane groove 100, respectively.

[0043] It should be noted that by constructing a vertically intersecting grid-like damping dissipation system, the longitudinal constraint effectively suppresses the transverse vibration transmission path, and works in conjunction with the first buffer rib 300 to achieve omnidirectional vibration isolation.

[0044] like Figures 2-3 As shown, there are no fewer than three second buffer ribs 400 between two adjacent first buffer ribs 300, and the number of second buffer ribs 400 is odd.

[0045] It should be noted that an odd number of ribs naturally creates a centrally symmetrical structure, eliminating the risk of paired resonance that may be caused by an even number of ribs; the design of no less than three ribs significantly increases the number of energy dissipation nodes per unit area, and significantly improves the dispersion and absorption capacity of high-frequency micro-amplitude vibrations.

[0046]

[0047] Experimental results demonstrate that the designed decoupling membrane can provide a larger damping angle and reduce dynamic stiffness to improve suspension damping performance. Real-vehicle testing showed no abnormal noises, and it effectively reduced aftershake vibrations, thus improving NVH comfort.

[0048] The above embodiments are only used to illustrate the technical methods of this utility model and are not intended to limit it. Although this utility model has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical methods of this utility model without departing from the spirit and scope of the technical methods of this utility model.

Claims

1. A suspended decoupling membrane structure for reducing dynamic stiffness, the suspended decoupling membrane structure comprising a membrane body (200) located within a flow channel decoupling membrane groove (100), characterized in that, The upper and lower surfaces of the diaphragm body (200) are respectively provided with a plurality of first buffer ribs (300) evenly distributed along the length direction. Between two adjacent first buffer ribs (300), a plurality of second buffer ribs (400) are provided along the width direction of the diaphragm body (200), and the length direction of the second buffer ribs (400) is perpendicular to the length direction of the first buffer ribs (300). The side of the first buffer ribs (300) and the second buffer ribs (400) away from the diaphragm body (200) respectively abuts against the top cover plate (500) of the flow channel decoupling membrane groove (100) and the bottom of the flow channel decoupling membrane groove (100).

2. The suspended decoupling membrane structure for reducing dynamic stiffness according to claim 1, characterized in that, The diaphragm body (200) includes a semi-circular portion (201) and a rectangular portion (202). The two semi-circular portions (201) are respectively disposed at both ends of the rectangular portion (202), and the semi-circular portions (201) and the rectangular portion (202) are integrally formed.

3. The suspended decoupling membrane structure for reducing dynamic stiffness according to claim 1, characterized in that, The first buffer rib (300) and the second buffer rib (400) have the same structure, and both the first buffer rib (300) and the second buffer rib (400) are composed of an abutment part (301), a transition part (302) and a support part (303). The support part (303) is connected to the diaphragm body (200). The transition part (302) is located on the side of the support part (303) away from the diaphragm body (200). The abutment part (301) is located on the side of the transition part (302) away from the support part (303). The abutment part (301), the transition part (302) and the support part (303) are integrally formed.

4. A suspension decoupling membrane structure for reducing dynamic stiffness according to claim 3, characterized in that, The abutting portion (301) includes a strip-shaped protrusion (3011) and an end protrusion (3012). The strip-shaped protrusion (3011) has a semi-cylindrical structure, and the end protrusion (3012) has a quarter-spherical structure. The two end protrusions (3012) are disposed at both ends of the strip-shaped protrusion (3011). The abutting portion (301) has the same facing side as the supporting portion (303) and the same cross-section as the transition portion (302).

5. A suspension decoupling membrane structure for reducing dynamic stiffness according to claim 3, characterized in that, The cross-section of the support (303) gradually decreases from the direction away from the diaphragm body (200), and the side of the support (303) is configured as a curved structure that gradually expands towards the diaphragm body (200).

6. A suspension decoupling membrane structure for reducing dynamic stiffness according to claim 1, characterized in that, The suspended decoupling membrane structure also includes a sealing ring (600), which is distributed circumferentially along the edge of the membrane body (200), and the height of the sealing ring (600) is flush with the depth of the flow channel decoupling membrane groove (100).

7. A suspension decoupling membrane structure for reducing dynamic stiffness according to claim 4, characterized in that, The cross-sectional radii of the strip protrusion (3011) and the end protrusion (3012) are equal.

8. A suspension decoupling membrane structure for reducing dynamic stiffness according to claim 1, characterized in that, The first buffer ribs (300) on the upper and lower surfaces of the diaphragm body (200) respectively abut against the first transverse rib (501) of the cover plate (500) and the second transverse rib (101) at the bottom of the flow channel decoupling membrane groove (100).

9. A suspension decoupling membrane structure for reducing dynamic stiffness according to claim 1, characterized in that, The second buffer ribs (400) on the upper and lower surfaces of the diaphragm body (200) respectively abut against the first longitudinal rib (502) of the cover plate (500) and the second longitudinal rib (102) at the bottom of the flow channel decoupling membrane groove (100).

10. A suspension decoupling membrane structure for reducing dynamic stiffness according to claim 1, characterized in that, There are no fewer than three second buffer ribs (400) between two adjacent first buffer ribs (300), and the number of second buffer ribs (400) is odd.

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