An asymmetric motor suspension

Abstract

The application discloses an asymmetric motor suspension, which comprises a bush outer framework and a bush inner framework, a bush rubber part is arranged between the inner wall of the bush outer framework and the outer wall of the bush inner framework, the bush rubber part comprises two first main spring legs and two second main spring legs which are centrally symmetrical, the stiffness of the first main spring leg and the second main spring leg is the same, and the first main spring leg and the second main spring leg are arranged in an asymmetric structure. The first main spring leg and the second main spring leg with the same stiffness but in an asymmetric structure can generate two low-frequency resonance peaks with low dynamic stiffness peaks under high-frequency vibration, compared with multiple high-frequency resonance peaks with high dynamic stiffness peaks in a symmetrical structure, so that the asymmetric motor suspension can play a good damping and buffering effect and inhibit the generation of motor high-frequency whistling. Meanwhile, the dynamic stiffness peak of the asymmetric motor suspension at high frequency can be attenuated after the generation of the two low-frequency resonance peaks, so that the generation of motor high-frequency whistling is further inhibited, and better vehicle NVH performance is obtained.

Description

Technical Field

[0001] This invention belongs to the field of suspension technology, and particularly relates to an asymmetrical motor suspension. Background Technology

[0002] Suspension components are one of the essential parts of a car chassis. Their main function is to connect the motor and the chassis, isolate vibrations from the road surface, reduce high-frequency resonance of the motor, and enhance the overall vehicle comfort.

[0003] In the current field, motors have a relatively wide frequency range at high frequencies. High-frequency states can cause the rubber suspension of the motor to resonate, resulting in increased rubber stiffness and thus causing high-frequency whistling from the motor. Summary of the Invention

[0004] To address the problems in the prior art, the present invention proposes the following technical solution:

[0005] An asymmetric motor suspension includes an outer bushing frame and an inner bushing frame. A bushing rubber component is disposed between the inner wall of the outer bushing frame and the outer wall of the inner bushing frame. The bushing rubber component includes two first main spring legs and two second main spring legs that are centrally symmetrical, and the first and second main spring legs have the same stiffness. The first and second main spring legs are asymmetrically arranged. The horizontal tilt angle α of the center of gravity of the first and second main spring legs is 20.8° to 21.8°, and the peak frequency ratio of the first and second main spring legs is 1.230 to 1.232. K is the stiffness, K = N * b * c / a, where N is the material hardness coefficient, b is the width of the main spring leg, c is the height of the main spring leg, a is the length of the main spring leg, and M is the mass of the main spring leg, M = a * b * c * P, where P is the material density.

[0006] This invention employs a first and second main spring leg with the same stiffness but asymmetrical, resulting in two low-frequency resonance peaks with lower dynamic stiffness peaks under high-frequency vibration. Compared to the multiple high-frequency resonance peaks with higher dynamic stiffness peaks in a symmetrical structure, this provides a good vibration damping and buffering effect, suppressing the generation of high-frequency motor whistling. At the same time, the high-frequency dynamic stiffness peaks in the asymmetrical structure of this invention will attenuate after the appearance of the two low-frequency resonance peaks, further suppressing the generation of high-frequency motor whistling, thereby achieving better overall vehicle NVH performance.

[0007] As a preferred embodiment of the above technical solution, the bushing inner skeleton includes an inner skeleton ring and an outer skeleton ring, and multiple connecting parts are integrally provided between the inner skeleton ring and the outer skeleton ring.

[0008] The structure that connects the inner and outer rings of the skeleton with multiple connecting parts creates multiple cavities in the middle, which has a good weight reduction effect compared to a solid structure.

[0009] As a preferred embodiment of the above technical solution, the outer ring of the skeleton is processed into an irregular shape to fit the end of the first main spring leg and the second main spring leg away from the inner sidewall of the bushing outer skeleton.

[0010] As a preferred embodiment of the above technical solution, the inner ring of the skeleton is provided with a mounting hole at its center.

[0011] As a preferred embodiment of the above technical solution, the bushing rubber component further includes a second impact block disposed on the inner ring wall of the bushing outer skeleton and a first impact block disposed on the front side.

[0012] The first and second impact blocks are used to prevent abnormal noises during impacts, making the motor move more smoothly.

[0013] As a preferred embodiment of the above technical solution, the horizontal tilt angle α of the center of gravity of the first main spring leg and the second main spring leg is 21.3°.

[0014] As a preferred embodiment of the above technical solution, the peak frequency ratio of the first main spring leg and the second main spring leg is 1.231.

[0015] The beneficial effects of this invention are as follows:

[0016] This invention employs a first and second main spring leg with the same stiffness but asymmetrical, resulting in two low-frequency resonance peaks with lower dynamic stiffness peaks under high-frequency vibration. Compared to the multiple high-frequency resonance peaks with higher dynamic stiffness peaks in a symmetrical structure, this provides a good vibration damping and buffering effect, suppressing the generation of high-frequency motor whistling. At the same time, the high-frequency dynamic stiffness peaks in the asymmetrical structure of this invention will attenuate after the appearance of the two low-frequency resonance peaks, further suppressing the generation of high-frequency motor whistling, thereby achieving better overall vehicle NVH performance. Attached Figure Description

[0017] Figure 1 The diagram shown is a three-dimensional structural schematic of the present invention;

[0018] Figure 2 The diagram shown is a front view of the structure of the present invention;

[0019] Figure 3 The diagram shown is a structural schematic of the first main spring leg in this invention;

[0020] Figure 4 The diagram shown is a structural schematic of the second main spring leg in this invention;

[0021] Figure 5 The diagram shown is a dynamic stiffness-frequency grid diagram with different stiffness ratios in this invention;

[0022] Figure 6 The diagram shown is a dynamic stiffness-frequency grid diagram at different frequency ratios in this invention;

[0023] Figure 7 The diagram shown is a dynamic stiffness-frequency grid diagram for a symmetrical structure.

[0024] Figure 8 The diagram shown is a dynamic stiffness-frequency grid diagram in an embodiment of the present invention.

[0025] Figure Labels

[0026] 10. Outer frame of bushing; 20. Inner frame of bushing; 21. Inner ring of frame; 22. Connecting part; 23. Outer ring of frame; 30. Bushing rubber part; 31. First main spring leg; 32. Second main spring leg; 33. First impact block; 34. Second impact block. Detailed Implementation

[0027] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the present invention will be clearly and completely described below in conjunction with the embodiments.

[0028] like Figures 1-4 As shown, Figure 1 The diagram shown is a three-dimensional structural schematic of the present invention; Figure 2 The diagram shown is a front view of the structure of the present invention; Figure 3 The diagram shown is a structural schematic of the first main spring leg 31 in this invention; Figure 4 The diagram shown is a structural schematic of the second main spring leg 32 in this invention.

[0029] The device includes an outer bushing frame 10 and an inner bushing frame 20. A bushing rubber component 30 is provided between the inner wall of the outer bushing frame 10 and the outer wall of the inner bushing frame 20. The bushing rubber component 30 includes two first main spring legs 31 and two second main spring legs 32 that are centrally symmetrical. The first main spring legs 31 and the second main spring legs 32 have the same stiffness. The first main spring legs 31 and the second main spring legs 32 are arranged in an asymmetrical structure.

[0030] like Figures 5-6 As shown, Figure 5 The diagram shown is a dynamic stiffness-frequency grid diagram with different stiffness ratios in this invention; Figure 6 The diagram shown is a dynamic stiffness-frequency grid diagram at different frequency ratios in this invention.

[0031] The horizontal tilt angle α of the center of gravity of the first main spring leg 31 and the second main spring leg 32 is 20.8° to 21.8°, and the peak frequency ratio of the first main spring leg 31 and the second main spring leg 32 is 1.230 to 1.232.

[0032] K is the stiffness, K = N * b * c / a, where N is the material hardness coefficient, b is the width of the main spring leg, c is the height of the main spring leg, a is the length of the main spring leg, and M is the mass of the main spring leg, M = a * b * c * P, where P is the material density.

[0033] This invention employs a first main spring leg 31 and a second main spring leg 32 with the same stiffness but asymmetrical, resulting in two low-frequency resonance peaks with lower dynamic stiffness peaks under high-frequency vibration, and high-frequency resonance peaks with higher dynamic stiffness peaks compared to the multiple dynamic stiffness peaks of a symmetrical structure (e.g., Figure 7 As shown, Figure 7 The diagram shown is a dynamic stiffness-frequency grid diagram under a symmetrical structure, which can play a good role in vibration reduction and buffering, suppressing the generation of high-frequency motor noise; at the same time, in the asymmetrical structure of the present invention, after the appearance of two low-frequency resonance peaks, the high-frequency dynamic stiffness peak will be attenuated, further suppressing the generation of high-frequency motor noise, thereby obtaining better overall vehicle NVH performance.

[0034] The bushing inner skeleton 20 includes an inner skeleton ring 21 and an outer skeleton ring 23. Multiple connecting parts 22 are integrally provided between the inner skeleton ring 21 and the outer skeleton ring 23. The structure of connecting the inner skeleton ring 21 and the outer skeleton ring 23 with multiple connecting parts 22 will form multiple cavities in the middle, which will have a good weight reduction effect compared with a solid structure.

[0035] The outer ring 23 of the skeleton is machined into an irregular shape to fit the end of the first main spring leg 31 and the second main spring leg 32 away from the inner sidewall of the bushing outer skeleton 10; the center of the inner ring 21 of the skeleton is machined with a mounting hole.

[0036] The bushing rubber component 30 also includes a second impact block 34 disposed on the inner ring wall of the bushing outer skeleton 10 and a first impact block 33 disposed on the front side; the first impact block 33 and the second impact block 34 are used to prevent abnormal noises from being generated during impact, so that the motor moves more smoothly.

[0037] Example

[0038] The horizontal tilt angle α of the center of gravity of the first main spring leg 31 and the second main spring leg 32 is 21.3°, and the peak frequency ratio of the first main spring leg 31 and the second main spring leg 32 is 1.231; its dynamic stiffness-frequency grid diagram is as follows. Figure 8 As shown.

[0039] For the first main spring leg 31: a = 24, b = 28, c = 61;

[0040] K = N*b*c / a = 71, M = a*b*c*P = 40924.8, peak frequency = 417Hz;

[0041] For the second main spring leg 32: a = 20, b = 24, c = 58;

[0042] K = N*b*c / a = 71, M = a*b*c*P = 26956.8, peak frequency = 513Hz;

[0043] Frequency ratio = 513 / 416 = 1.231

[0044] Stiffness ratio (i.e., y:x, the total stiffness of the main spring leg is distributed to the x-axis and y-axis according to the stiffness ratio): α is 21.3°, tan21.3°=0.390.

[0045] In conjunction with the embodiments, in the embodiment where the frequency ratio is 1.231 and the stiffness ratio is 0.39, the two peak resonant frequencies of the motor suspension component of the asymmetric structure of the present invention are 417Hz and 513Hz, and the dynamic stiffness corresponding to the peak frequencies is low. After the two low-frequency resonant peaks appear, the high-frequency dynamic stiffness peak will decay.

[0046] The above embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit it.

Claims

1. An asymmetric motor suspension, comprising an outer bushing frame (10) and an inner bushing frame (20), wherein a bushing rubber component (30) is disposed between the inner wall of the outer bushing frame (10) and the outer wall of the inner bushing frame (20), characterized in that, The bushing rubber component (30) includes two first main spring legs (31) and two second main spring legs (32) that are centrally symmetrical, and the first main spring legs (31) and the second main spring legs (32) have the same stiffness. The first main spring legs (31) and the second main spring legs (32) are arranged in an asymmetrical structure. The horizontal tilt angle α of the center of gravity of the first main spring legs (31) and the second main spring legs (32) is 20.8° to 21.8°. The peak frequency ratio of the first main spring legs (31) and the second main spring legs (32) is 1.230 to 1.

232. K is the stiffness, K = N * b * c / a, where N is the material hardness coefficient, b is the width of the main spring leg, c is the height of the main spring leg, a is the length of the main spring leg, and M is the mass of the main spring leg, M = a * b * c * P, where P is the material density.

2. The asymmetric motor suspension according to claim 1, characterized in that, The bushing inner skeleton (20) includes an inner skeleton ring (21) and an outer skeleton ring (23), and multiple connecting parts (22) are integrally provided between the inner skeleton ring (21) and the outer skeleton ring (23).

3. An asymmetric motor suspension according to claim 2, characterized in that, The outer ring (23) of the skeleton is processed into an irregular shape to fit the end of the first main spring leg (31) and the second main spring leg (32) away from the inner wall of the bushing outer skeleton (10).

4. An asymmetric motor suspension according to claim 2, characterized in that, The inner ring (21) of the skeleton has a mounting hole machined in its center.

5. An asymmetric motor suspension according to claim 1, characterized in that, The bushing rubber component (30) also includes a second impact block (34) disposed on the inner ring wall of the bushing outer skeleton (10) and a first impact block (33) disposed on the front side.

6. An asymmetric motor suspension according to claim 1, characterized in that, The horizontal tilt angle α of the center of gravity of the first main spring leg (31) and the second main spring leg (32) is 21.3°.

7. An asymmetric motor suspension according to claim 6, characterized in that, The peak frequency ratio of the first main spring leg (31) and the second main spring leg (32) is 1.231.

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