Acceleration amplification device based on lever amplification principle

Abstract

The utility model discloses an acceleration amplification device based on a lever amplification principle, and relates to the technical field of acceleration amplification devices. Comprising a cross beam, a first support, a second support, a connecting piece, a first flexible hinge and a second flexible hinge, the cross beam is a variable cross-section rigid beam, the measuring sensor is installed at the tail end of one end of the cross beam, the first flexible hinge and the second flexible hinge are both fixedly connected with the cross beam, the first flexible hinge is further fixedly connected with the connecting piece, the connecting piece is detachably connected with the second support, the second flexible hinge is further fixedly connected with the first support, and the first support is fixedly connected with the vibration table. The second flexible hinge is located between the first flexible hinge and the vibration sensor, and the distance between the first flexible hinge and the second flexible hinge is smaller than the distance between the second flexible hinge and the vibration sensor. According to the utility model, the conventional vibration acceleration can be amplified without being influenced by the installation times and the load, and the calibration of the vibration sensor during high-acceleration vibration is completed.

Description

An acceleration amplification device based on the lever amplification principle Technical Field

[0001] This utility model belongs to the technical field of acceleration amplification devices, and more specifically, it relates to an acceleration amplification device based on the lever amplification principle. Background Technology

[0002] Vibration sensors are widely used in aerospace, machinery manufacturing, marine and vehicle industries for acceleration measurement. Some high-acceleration vibration sensors have a measurement range up to 5000 m / s². 2 Even 10000m / s 2 Currently, the acceleration amplitude of a standard shaking table generally does not exceed 400 m / s². 2 The acceleration amplitude of an electric vibration table generally does not exceed 1000 m / s². 2 It is difficult to calibrate the full acceleration range using vibration methods. The industry primarily uses impact calibration to obtain the sensitivity and linearity of these high-acceleration vibration sensors. However, this method cannot obtain the frequency response performance of the vibration sensor, and its sensitivity under vibration conditions still has certain systematic errors, thus having limitations. To address this, some researchers have developed resonant excitation devices based on the resonance principle, solving the problem of insufficient vibration acceleration amplitude in the mid-to-high frequency range. However, this is still insufficient for exciting high vibration acceleration in the mid-to-low frequency range, and the amplification factor of the resonant excitation device is affected by installation conditions and load mass, which is not conducive to practical metrology work. Summary of the Invention

[0003] The technical problem to be solved by this utility model is to provide an acceleration amplification device based on the lever amplification principle, which can amplify existing vibration acceleration, is not affected by the number of installations and the load, and complete the calibration of vibration sensors under high acceleration vibration.

[0004] To solve the above-mentioned technical problems, the technical solution adopted by this utility model is: an acceleration amplification device based on the lever amplification principle, including a crossbeam, a first support, a second support, a connector, a first flexible hinge, and a second flexible hinge; the crossbeam is a variable cross-section rigid beam, and a vibration sensor is installed at one end of the crossbeam; one end of the first flexible hinge and the second flexible hinge are both fixedly connected to the other end of the crossbeam; the other end of the first flexible hinge is fixedly connected to the connector, and the connector is detachably connected to the second support; the other end of the second flexible hinge is fixedly connected to the first support; the first support is fixedly connected to a vibration table; the first flexible hinge is located at the end of the crossbeam; the second flexible hinge is located between the first flexible hinge and the vibration sensor, and the distance between the first flexible hinge and the second flexible hinge is less than the distance between the second flexible hinge and the vibration sensor.

[0005] Preferably, the cross-section of the crossbeam is in the shape of an "I" or a "U".

[0006] Preferably, the beam is divided into two sections along its length: one section is a beam with a constant cross-section, and the other section is a beam with a variable cross-section whose cross-sectional area gradually decreases along its length. The two sections have the same cross-sectional shape.

[0007] Preferably, the first flexible hinge is a cuboid structure made of spring steel 60Si2MnA. The length direction of the cuboid is consistent with the length direction of the beam. A through groove with an arc cross-section is dug on both parallel side surfaces of the cuboid along the width direction of the cuboid. The two through grooves are symmetrically arranged, and the central axis of the through groove is parallel to the width direction of the cuboid.

[0008] Preferably, the second flexible hinge is a cuboid structure made of spring steel 60Si2MnA. The length direction of the cuboid is consistent with the length direction of the beam. A through groove with an arc cross-section is excavated on both parallel side surfaces of the cuboid along the width direction of the cuboid. The two through grooves are symmetrically arranged, and the central axis of the through groove is parallel to the width direction of the cuboid.

[0009] Preferably, the first flexible hinge is a cross-spring type flexible hinge, which is obtained by two thin strips that are distributed in pairs at a certain angle to the horizontal direction, and the material used is spring steel 60Si2MnA.

[0010] Preferably, the second flexible hinge is a cross-spring type flexible hinge, which is obtained by four thin strips at a certain angle to the horizontal direction, distributed in pairs, and the material used is spring steel 60Si2MnA.

[0011] The beneficial effects of adopting the above technical solution are as follows:

[0012] 1. In this application, both the first flexible hinge and the second flexible hinge adopt a cuboid structure with arc-shaped through grooves on both sides. The area between the two arc-shaped through grooves is the weak point of the hinge. Under the action of torque, the flexible hinge will bend and rotate at the weak point. Compared with traditional hinges, there are no disadvantages such as gaps and friction, which improves the accuracy of vibration experiments.

[0013] 2. The amplification factor of this amplification device is fixed before the input frequency is lower than the natural frequency, and it mainly amplifies acceleration in the low to mid-frequency range. Compared with resonant excitation devices, when the natural frequency of this device is much higher than the operating frequency, its amplification factor is basically unaffected by the load, natural frequency, etc., making it easier to carry out practical applications. Attached Figure Description

[0014] Figure 1 is a schematic diagram of the overall structure;

[0015] Figure 2 is a schematic diagram of the structure of the first embodiment of the amplification device;

[0016] Figure 3 is a schematic diagram of the second embodiment of the amplification device.

[0017] Figure 4 is a schematic diagram of the main structure of the second embodiment of the magnification device;

[0018] Figure 5 is a magnification curve obtained when different weight sensors are installed in the second embodiment;

[0019] Figure 6 is a schematic diagram of the rotation state of the flexible hinge in the second embodiment;

[0020] Figure 7 is a schematic diagram of the dimensions of the crossbeam.

[0021] In the figure: 1. Vibration sensor; 2. Crossbeam; 3. First support; 4. Vibration table; 5. Second support; 6. Connector; 7. First flexible hinge; 8. Second flexible hinge. Detailed Implementation

[0022] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.

[0023] As shown in Figure 1, the amplification device includes a crossbeam 2, a first support 3, a second support 5, a connector 6, a first flexible hinge 7, and a second flexible hinge 8. The crossbeam 2 is a rigid beam with a variable cross-section. A vibration sensor 1 is installed at one end of the crossbeam 2, and the other end is sequentially connected to the first flexible hinge 7 and the second flexible hinge 8. The other end of the first flexible hinge 7 is fixedly connected to the connector 6, which is detachably connected to the second support 5 via bolts, facilitating the removal of the amplification device from the second support 5. The other end of the second flexible hinge 8 is fixedly connected to the first support 3, and the first support 3 is fixedly connected to a vibration table 4. A control sensor is installed on the vibration table 4, which provides vibration displacement. The vibration frequency of the vibration table 4 is lower than the natural frequency of the crossbeam 2. The second flexible hinge 8 is located between the first flexible hinge 7 and the measuring sensor 1, and the distance between the first flexible hinge 7 and the second flexible hinge 8 is less than the distance between the second flexible hinge 8 and the vibration sensor 1. Note that the crossbeam 2 is divided into two sections: one is a beam with a variable cross-section, and the other has a constant cross-section. The first flexible hinge 7 and the second flexible hinge 8 are installed on the section of the crossbeam 2 with an unchanged cross section.

[0024] In the first embodiment, as shown in Figure 2, the first flexible hinge 7 and the second flexible hinge 8 are cross-type spring flexible hinges. This hinge has a large rotational stroke and a large rotational angle. When the displacement input to the vibration table 4 is large, the hinge needs to withstand a larger rotational angle, making the cross-type spring flexible hinge suitable. In this case, the crossbeam 2 is a variable cross-section U-shaped beam. When the input frequency is low, a larger displacement is required to achieve the same acceleration. To obtain a larger output acceleration at a lower frequency, the hinge also needs to have a large rotational stroke, and the cross-type spring flexible hinge is more suitable.

[0025] In the second embodiment, as shown in Figure 3, the first flexible hinge 7 and the second flexible hinge 8 are flexible hinges with two arc-shaped through slots. The bending and rotation point is located between the two arc-shaped through slots, and the vibration bending state is shown in Figure 6. At this time, the crossbeam 2 is an I-beam. The crossbeam 2, the first flexible hinge 7, the second flexible hinge 8, the first support 3, and the connector 6 are integrated into one unit, manufactured using wire cutting technology, and the material is 60Si2MnA spring steel. The specific dimensions are shown in Figure 4. The length of the variable cross-section section of the crossbeam 2 is L1=200mm, the length of the uniform cross-section section is L2=41mm, the length of the first flexible hinge 7 and the second flexible hinge 8 is B2=14mm, the distance from the bottom of the arc-shaped through groove to the end face of the uniform cross-section section is L3=6.5mm, the thickness of the rotating part of the flexible hinge is B1=1mm, the distance from the bottom of the arc-shaped through groove to the bottom surface of the crossbeam 2 is H3=5mm, the dimensions of the cross-section of the large end (uniform cross-section section) of the crossbeam 2 are shown in Figure 7, A2=10mm, H2=14mm, b2=3mm, and the dimensions of the small end (where the vibration sensor 1 is installed) are shown in Figure 7, A1=2.5mm, H1=3.5mm, b1=0.75mm.

[0026] Technicians conducted experiments on the second embodiment and obtained the relationship curve between the amplification factor and the input frequency, as shown in Figure 5. Figure 5 shows that the amplification factor of the second embodiment is largely unaffected by the number of installations and the load before the natural frequency, exhibiting good repeatability.

[0027] The experimental results of the peak output acceleration of the device are shown in the table below.

[0028] Frequency (Hz) Sensor Mass (g) Input Acceleration (m / s²) Output Acceleration (m / s²) 80 10.5 97.5 31 107 160 1.0 14 0.7 20 23 surface

[0029] As can be seen from the table above, the output acceleration under different loads far exceeds the input acceleration, which has a good amplification effect.

[0030] In summary, this invention, based on the lever amplification principle, excites high acceleration by amplifying displacement, solving the problem of low vibration acceleration amplitude in the mid-to-low frequency range. Furthermore, the amplification factor of this device is fixed before the natural frequency, facilitating measurement work. This invention supplements and improves upon current high vibration acceleration excitation devices.

[0031] The above are merely preferred embodiments of this utility model, but the scope of protection of this utility model is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in this utility model, based on the technical solution and inventive concept of this utility model, should be included within the scope of protection of this utility model.

Claims

1. An acceleration amplification device based on the lever amplification principle, characterized in that, It includes a cross beam (2), a first support (3), a second support (5), a connecting member (6), a first flexible hinge (7), and a second flexible hinge (8); the cross beam (2) is a rigid beam with a variable cross-section. A vibration sensor (1) is installed at the end of one end of the cross beam (2). One ends of the first flexible hinge (7) and the second flexible hinge (8) are fixedly connected to the other end of the cross beam (2). The other end of the first flexible hinge (7) is fixedly connected to the connecting member (6), and the connecting member (6) is detachably connected to the second support (5). The other end of the second flexible hinge (8) is fixedly connected to the first support (3), and the first support (3) is fixedly connected to the vibration table (4). The first flexible hinge (7) is located at the end of the cross beam (2), and the second flexible hinge (8) is located between the first flexible hinge (7) and the vibration sensor (1), and the distance between the first flexible hinge (7) and the second flexible hinge (8) is less than the distance between the second flexible hinge (8) and the vibration sensor (1).

2. The acceleration amplification device based on the lever amplification principle according to claim 1, characterized in that, The cross-section of the cross beam (2) is in the shape of "I" or "□".

3. An acceleration amplification device based on the lever amplification principle according to claim 2, characterized in that, The cross beam (2) is divided into two segments along the length direction. One segment is a beam with a constant cross-section, and the other segment is a variable cross-section beam whose cross-sectional area gradually decreases along the length direction. The cross-sectional shapes of the two segments are the same.

4. An acceleration amplification device based on the lever amplification principle according to claim 1, characterized in that, The first flexible hinge (7) is a cuboid structure made of spring steel 60Si2MnA. The length direction of the cuboid is the same as the length direction of the cross beam (2). Through grooves with an arc-shaped cross-section are dug along the width direction on the two parallel side vertical surfaces of the cuboid. The two through grooves are symmetrically arranged, and the central axis of the through groove is parallel to the width direction of the cuboid.

5. An acceleration amplification device based on the lever amplification principle according to claim 1, characterized in that, The second flexible hinge (8) is a cuboid structure made of spring steel 60Si2MnA. The length direction of the cuboid is the same as the length direction of the cross beam (2). Through grooves with an arc-shaped cross-section are dug along the width direction on the two parallel side vertical surfaces of the cuboid. The two through grooves are symmetrically arranged, and the central axis of the through groove is parallel to the width direction of the cuboid.

6. An acceleration amplification device based on the lever amplification principle according to claim 1, characterized in that, The first flexible hinge (7) is a cross-spring flexible hinge, which is obtained by cross-distributing 4 thin strips at a certain angle with the horizontal direction and is made of spring steel 60Si2MnA.

7. An acceleration amplification device based on the lever amplification principle according to claim 1, characterized in that, The second flexible hinge (8) is a cross-spring flexible hinge, which is obtained by cross-distributing 4 thin strips at a certain angle with the horizontal direction and is made of spring steel 60Si2MnA.

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