Stepless amplitude-variable reciprocating driving mechanism and design method thereof, fascia gun

Abstract

The present application relates to fascia gun technical field, disclose a kind of stepless amplitude reciprocating drive mechanism and its design method, fascia gun, to solve the problem of low efficiency existing in prior art design method, stepless amplitude reciprocating drive mechanism includes the slider-crank mechanism by eccentric wheel, output rod, connecting rod and slider are sequentially articulated and adjustment rod, the swing end of adjustment rod is articulated on output rod, the position of the adjustment end of adjustment rod is adjustable, and after adjustment, the swing range of second articulation point is limited, method includes: determining the first distance between first articulation point and second articulation point, the second distance between second articulation point and third articulation point, the third distance between third articulation point and fourth articulation point and the functional relationship between the position of fifth articulation point and slider amplitude, and the design of stepless amplitude reciprocating drive mechanism is carried out based on functional relationship.The present application improves the design efficiency and accuracy of stepless amplitude reciprocating drive mechanism, and is suitable for fascia gun product.

Description

Technical Field

[0001] This invention relates to the field of fascia gun technology, specifically to a continuously variable amplitude reciprocating drive mechanism and its design method, and a fascia gun. Background Technology

[0002] A fascia gun, also known as a deep myofascial release device, is a soft tissue massage tool that relaxes the body's soft tissues through high-frequency impacts. Current fascia guns use a piston to drive the massage head in a linear reciprocating motion. The massage head contacts the body, generating high-frequency vibrations that penetrate deep into the muscles, reducing local tissue tension, relieving pain, and promoting blood circulation. Existing fascia guns now feature adjustable massage head amplitude, allowing users to choose the appropriate amplitude and depth for their massage therapy. For example, professional athletes require a larger amplitude to relieve muscle tension after exercise. Ordinary consumers, especially beginners, should initially use a fascia gun with a smaller amplitude and gradually increase it as needed.

[0003] Patent application CN202310288298X seeks protection for a continuously variable amplitude reciprocating drive mechanism and a fascia gun. Its main technical solution involves adding an amplitude adjustment mechanism to a crank-slider mechanism, which consists of a crank, output rod, connecting rod, and slider sequentially hinged. The amplitude adjustment mechanism adjusts and limits the swing range of the hinge point between the output rod and the connecting rod, thereby simplifying the amplitude adjustment structure and ensuring stability after amplitude adjustment. In the aforementioned continuously variable amplitude reciprocating drive mechanism, the slider amplitude changes complexly due to the influence of the position and length of the crank, output rod, connecting rod, and adjusting rod. To design a continuously variable amplitude reciprocating drive mechanism that meets the amplitude and dimensional requirements, the common approach is to establish a three-dimensional simulation model of the mechanism and repeatedly adjust the position and length of each structural component in the 3D simulation model to obtain the slider amplitude until the design requirements are met. This method is complex and inefficient due to the need to establish and repeatedly adjust the 3D simulation model. Summary of the Invention

[0004] This invention aims to solve the problem of low efficiency in the existing design methods of continuously variable amplitude reciprocating drive mechanisms, and proposes a continuously variable amplitude reciprocating drive mechanism and its design method, as well as a fascia gun.

[0005] The technical solution adopted by the present invention to solve the above-mentioned technical problems is as follows:

[0006] Firstly, a design method for a continuously variable amplitude reciprocating drive mechanism is proposed. The continuously variable amplitude reciprocating drive mechanism includes a crank-slider mechanism consisting of an eccentric wheel, an output rod, a connecting rod, and a slider connected in sequence, as well as an adjusting rod. The hinge point between the connecting rod and the slider is the first hinge point, the hinge point between the output rod and the connecting rod is the second hinge point, and the hinge point between the output rod and the eccentric wheel is the third hinge point. The adjusting rod has a swing end and an adjusting end. The swing end of the adjusting rod is hinged to the output rod through a fourth hinge point, and the hinge point of the adjusting end of the adjusting rod is the fifth hinge point. The position of the fifth hinge point is adjustable, and after adjustment, it limits the swing range of the second hinge point.

[0007] The method includes: determining the functional relationship between the first distance between the first hinge point and the second hinge point, the second distance between the second hinge point and the third hinge point, the third distance between the third hinge point and the fourth hinge point, and the position of the fifth hinge point and the slider amplitude, and designing a continuously variable amplitude reciprocating drive mechanism based on the functional relationship.

[0008] In the aforementioned continuously variable amplitude reciprocating drive mechanism, since the slider is rotatably connected to the connecting rod, and the connecting rod and adjusting rod are rotatably connected to the output rod respectively, the connecting rod and adjusting rod will move with the swing of the output rod, thereby causing the slider to move. In actual design, the swing range of the second hinge point can be changed by adjusting the rotational connection position of the adjusting end of the adjusting rod, or by adjusting the length of the output rod and the connecting rod, thereby changing the slider amplitude. This invention establishes a functional relationship between the position of the first distance, the second distance, the third distance, and the fifth hinge point and the slider amplitude. When designing the aforementioned continuously variable amplitude reciprocating drive mechanism, the rotational connection position of the adjusting end of the adjusting rod and the length of the output rod and the connecting rod that satisfy the functional relationship can be selected according to the design requirements, or the slider amplitude can be verified based on the functional relationship. This eliminates the need to establish a three-dimensional simulation model and repeatedly adjust the three-dimensional simulation model, simplifying the design operation and improving design efficiency.

[0009] Furthermore, the method for determining the functional relationship includes:

[0010] Construct a planar model of the continuously variable amplitude reciprocating drive mechanism;

[0011] In the planar model, a rectangular coordinate system is established with the rotation input end of the eccentric wheel as the origin;

[0012] Based on the Cartesian coordinate system, the functional relationship between the position coordinates of the first distance, the second distance, the third distance, and the fifth hinge point and the slider amplitude is determined.

[0013] This invention can improve the efficiency and accuracy of determining the functional relationship by constructing a planar model of a continuously variable reciprocating drive mechanism, building a rectangular coordinate system in the planar model, and determining the functional relationship based on the rectangular coordinate system. At the same time, the rotational connection position of the adjusting end of the adjusting rod is reflected by the coordinates in the rectangular coordinate system.

[0014] Furthermore, the method for determining the functional relationship specifically includes:

[0015] Determine the left and right limit points of the third hinge point when it rotates at the rotation input end of the eccentric wheel;

[0016] A first calculation formula is used to calculate the fourth distance between the first hinge point and the third hinge point by determining the first distance, the second distance, the third distance, the position coordinates of the fifth hinge point and the position coordinates of the third hinge point;

[0017] The second calculation formula for the maximum fourth distance is obtained by substituting the coordinates of the left limit point as the coordinates of the third hinge point into the first calculation formula, and the third calculation formula for the minimum fourth distance is obtained by substituting the coordinates of the right limit point as the coordinates of the third hinge point into the first calculation formula.

[0018] The function relationship is obtained by subtracting the second calculation formula from the third calculation formula.

[0019] In the aforementioned continuously variable amplitude reciprocating drive mechanism, when the eccentric wheel rotates, it causes a change in the position of the third hinge point. When the third hinge point is at the left extreme point, the slider has the maximum distance relative to the third hinge point; when the third hinge point is at the right extreme point, the slider has the minimum distance relative to the third hinge point. The difference between the maximum and minimum distances is the slider amplitude. Based on this, the present invention can determine the first calculation formula for calculating the fourth distance in a rectangular coordinate system, and then substitute the position coordinates of the left and right extreme points into the first calculation formula and take the difference to obtain the calculation formula for the slider amplitude. This calculation formula can then be used as the aforementioned functional relationship, thus further improving the efficiency and accuracy of determining the functional relationship.

[0020] Furthermore, the method for determining the first calculation formula is as follows:

[0021] Determine the fourth calculation formula for calculating the position coordinates of the fourth hinge point;

[0022] A fifth calculation formula is used to calculate the slope of the straight line containing the output rod by using the position coordinates of the fourth hinge point and the position coordinates of the third hinge point;

[0023] A sixth calculation formula for calculating the fourth distance using the slope, the first distance, and the second distance is determined. The fourth, fifth, and sixth calculation formulas are then combined to obtain the first calculation formula.

[0024] In a Cartesian coordinate system, the slope of the line containing the output rod can be determined using the coordinates of the fourth hinge point and the third hinge point. Therefore, within the triangle formed by the first, second, and third hinge points, the fourth distance can be determined based on the first distance, the second distance, and the slope of the line containing the output rod. Based on this, the present invention combines the calculation formulas for the above parameters to obtain a first calculation formula for the fourth distance, thus improving the efficiency and accuracy of determining the first calculation formula.

[0025] Furthermore, the method for determining the fourth calculation formula is as follows:

[0026] The equation of the first circle is determined with the center of the fifth hinge point and the radius of the fifth distance, where the fifth distance is the distance between the fourth hinge point and the fifth hinge point;

[0027] Determine the equation of the second circle with the center at the third hinge point and the radius at the second distance;

[0028] The system of equations formed by the first and second circle equations is used as the fourth calculation formula.

[0029] In the aforementioned continuously variable reciprocating drive mechanism, the fourth hinge point is the intersection of the output rod and the adjusting rod. Therefore, the fourth hinge point must be the intersection of the first circle and the second circle. Based on this, the present invention can obtain a fourth calculation formula for calculating the coordinates of the intersection point of the two circles through a system of equations consisting of the equations of the first circle and the second circle. The position coordinates of the fourth hinge point can be obtained through the coordinates of the intersection point, thus improving the efficiency and accuracy of determining the fourth calculation formula.

[0030] Furthermore, the equation of the first circle is as follows:

[0031] (x D -x E ) 2 +(y D -y E ) 2 =DE 2 ;

[0032] The equation of the second circle is as follows:

[0033] (x D -x C ) 2 +(y D -y C ) 2 =BC 2 ;

[0034] In the formula, x D Let y be the x-coordinate of the fourth hinge point. D Let x be the ordinate of the fourth hinge point. E Let y be the x-coordinate of the fifth hinge point. E Let x be the ordinate of the fifth hinge point. C Let y be the x-coordinate of the third hinge point. C Let y be the ordinate of the third hinge point, DE be the fifth distance, and BC be the second distance.

[0035] In the aforementioned continuously variable reciprocating drive mechanism, if the first, second, and third distances are fixed and the position of the fifth hinge point is fixed, then the fifth distance must also be fixed. Therefore, in practical applications, the fifth distance can be determined by the position coordinates of the fifth hinge point and the first, second, and third distances. The position coordinates of the third hinge point can be determined by the eccentricity of the eccentric wheel. For example, when the third hinge point is located at the left extreme point, its corresponding abscissa is less than 0 and its ordinate is 0; when the third hinge point is located at the right extreme point, its corresponding abscissa is greater than 0 and its ordinate is 0. Of course, when the relative coordinates of the left and right extreme points are rotated, the ordinates of the left and right extreme points may not be 0, but the specific calculation methods are the same. The relevant technical solutions after the angle rotation are not listed here. For ease of calculation, please refer to the specific technical solution proposed in this embodiment where the ordinates of the left and right extreme points are 0. Determining the circular equation in the above way can further improve the efficiency and accuracy of the fourth calculation formula.

[0036] Furthermore, the fifth calculation formula is as follows:

[0037]

[0038] The sixth calculation formula is as follows:

[0039] in:

[0040] ∠B = 180° - ∠A - ∠C

[0041] In the formula, k is the slope, x D Let y be the x-coordinate of the fourth hinge point. D Let x be the ordinate of the fourth hinge point. C Let y be the x-coordinate of the third hinge point. C Let y be the ordinate of the third hinge point, AC be the fourth distance, AB be the first distance, BC be the second distance, and ∠A, ∠B, and ∠C be the interior angles of the triangle formed by the first, second, and third hinge points, respectively.

[0042] In the aforementioned continuously variable reciprocating drive mechanism, both the third and fourth hinge points are located on the straight line of the output rod. Therefore, this invention can calculate the slope of the straight line of the output rod using the position coordinates of the third and fourth hinge points. Furthermore, in the triangle formed by the first, second, and third hinge points, the sum of all interior angles is 180 degrees. Thus, the fourth distance can be calculated based on the first distance, the second distance, and the slope of the straight line of the output rod. This method improves the efficiency and accuracy of the fifth and sixth calculation formulas.

[0043] Furthermore, the design of the continuously variable amplitude reciprocating drive mechanism based on the aforementioned functional relationship specifically includes:

[0044] Substitute the determined first distance, second distance, third distance, and fifth hinge point coordinates into the function relationship to calculate the slider amplitude, and determine whether the slider amplitude meets the design requirements.

[0045] In practical applications, the slider amplitude of the designed continuously variable reciprocating drive mechanism can be verified based on the functional relationship, thereby improving design efficiency.

[0046] Furthermore, the design of the continuously variable amplitude reciprocating drive mechanism based on the aforementioned functional relationship specifically includes:

[0047] Based on the slider amplitude determined according to the design requirements and the aforementioned functional relationship, adjust the positions of the first distance, the second distance, the third distance, and / or the fifth hinge point.

[0048] In practical applications, the length of the connecting rod, the length of the output rod, and / or the position of the fifth hinge point can be adjusted to make the continuously variable reciprocating drive mechanism achieve the slider amplitude required by the design, thereby improving the design efficiency.

[0049] Furthermore, the position of the fifth hinge point must at least satisfy the following conditions:

[0050] |DE-BC1|<CE<|DE+BC1|;

[0051] |DE-BC2|<CE<|DE+BC2|;

[0052] In the formula, CE is the sixth distance between the third hinge point and the fifth hinge point, DE is the fifth distance between the fourth hinge point and the fifth hinge point, BC1 is the seventh distance between the second hinge point and the left limit point, and BC2 is the eighth distance between the second hinge point and the right limit point.

[0053] When designing the continuously variable reciprocating drive mechanism and adjusting the position of the fifth hinge point, the above conditions should be met so that the output rod and the adjusting rod have an intersection point, thereby enabling the output rod and the adjusting rod to be rotatably connected through the fourth hinge point, which can further improve design efficiency.

[0054] Furthermore, the design of the continuously variable amplitude reciprocating drive mechanism based on the aforementioned functional relationship specifically includes:

[0055] Based on the determined range of slider amplitude variation, first distance, second distance, and third distance according to the design requirements and based on the functional relationship, multiple positions of the fifth hinge point are determined, and a position adjustment mechanism for the fifth hinge point is designed according to the multiple positions of the fifth hinge point.

[0056] In practical applications, the required slider amplitude may be a range. This invention can determine multiple positions of the fifth hinge point corresponding to this range based on functional relationships, and then design a position adjustment mechanism for the fifth hinge point, thereby improving the accuracy of the design.

[0057] Furthermore, the axis of the second hinge point is coaxial with the axis of the fourth hinge point.

[0058] In practical applications, the second and fourth hinge points in the continuously variable amplitude reciprocating drive mechanism can be located on the same axis. That is, in the planar model, the second and fourth hinge points coincide, and their position coordinates in the Cartesian coordinate system are the same. In this case, the same method described above can be used to design the continuously variable amplitude reciprocating drive mechanism. In practical applications, the second and fourth hinge points can be interchanged.

[0059] Secondly, a continuously variable amplitude reciprocating drive mechanism is proposed, comprising a crank-slider mechanism consisting of a crank, an output rod, a connecting rod, and a slider connected in sequence, and an adjusting rod. The crank is an eccentric wheel. The hinge point between the connecting rod and the slider is the first hinge point. The hinge point between the output rod and the connecting rod is the second hinge point. The hinge point between the connecting rod and the eccentric wheel is the third hinge point. The adjusting rod has a swing end and an adjusting end. The swing end of the adjusting rod is hinged to the output rod through a fourth hinge point. The hinge point of the adjusting end of the adjusting rod is the fifth hinge point. The position of the fifth hinge point is adjustable, and after adjustment, it limits the swing range of the second hinge point.

[0060] The continuously variable amplitude reciprocating drive mechanism is designed using the design method for continuously variable amplitude reciprocating drive mechanisms as described in the first aspect.

[0061] This invention establishes a functional relationship between the positions of the first distance, the second distance, the third distance, and the fifth hinge point and the slider amplitude. When designing the above-mentioned continuously variable reciprocating drive mechanism, the rotational connection position of the adjusting end of the adjusting rod and the length of the output rod and the connecting rod that satisfy the functional relationship can be selected according to the design requirements. Alternatively, the slider amplitude can be verified based on the functional relationship. There is no need to establish a three-dimensional simulation model, nor is it necessary to repeatedly adjust the three-dimensional simulation model, which simplifies the design operation and improves the design efficiency.

[0062] Furthermore, it also includes a position adjustment mechanism, wherein the adjustment end of the adjustment rod is hinged to the position adjustment mechanism, and the position adjustment mechanism drives the adjustment end of the adjustment rod to move relative to the position.

[0063] The position adjustment mechanism allows for convenient and reliable adjustment of the adjustment end position of the adjustment rod, thereby driving the adjustment rod to adjust the swing range of the second hinge point on the output rod, and thus realizing the adjustment of the slider amplitude.

[0064] Thirdly, a fascia gun is proposed, comprising a mounting cavity consisting of a lower shell, an upper shell, a front cover, and a rear cover, and a motor. The fascia gun also includes a continuously variable amplitude reciprocating drive mechanism as described in the second aspect. The slider is a piston, which is slidably disposed in the piston hole of the front cover. The rotation input end of the eccentric wheel is fixedly connected to the output shaft of the motor.

[0065] In practical applications, the space occupied by the continuously variable amplitude reciprocating drive mechanism can be evaluated based on the size of the fascia gun housing. Based on the evaluation results and functional relationships, the corresponding size of the connecting rod and output rod, as well as the corresponding hinge point position, can be selected, thereby improving design efficiency.

[0066] The beneficial effects of this invention are as follows: The continuously variable amplitude reciprocating drive mechanism and its design method, as well as the fascia gun described in this invention, establish a functional relationship between the position of the first distance, the second distance, the third distance, and the fifth hinge point and the slider amplitude. When designing the continuously variable amplitude reciprocating drive mechanism, the rotational connection position of the adjusting end of the adjusting rod and the lengths of the output rod and connecting rod that satisfy the functional relationship can be selected according to the design requirements. Alternatively, the slider amplitude can be verified based on the functional relationship, eliminating the need to establish a three-dimensional simulation model and repeatedly adjust it, thus simplifying the design operation and improving design efficiency. By creating a rectangular coordinate system in the planar model of the continuously variable amplitude reciprocating drive mechanism and establishing a functional relationship within that system, the efficiency and accuracy of determining the functional relationship are improved. In practical applications, the required slider amplitude may be a range. This invention can also determine multiple positions of the fifth hinge point corresponding to this range based on the functional relationship, thereby designing a position adjustment mechanism for the fifth hinge point, which further improves design accuracy. Attached Figure Description

[0067] Figure 1 This is a three-dimensional structural schematic diagram of the continuously variable amplitude reciprocating drive mechanism according to an embodiment of the present invention;

[0068] Figure 2 This is a schematic diagram of the planar structure of the continuously variable amplitude reciprocating drive mechanism according to an embodiment of the present invention;

[0069] Figure 3 This is a schematic diagram of the position adjustment mechanism described in an embodiment of the present invention;

[0070] Figure 4 This is a flowchart illustrating the design method of the continuously variable amplitude reciprocating drive mechanism according to an embodiment of the present invention.

[0071] Figure 5 This is a schematic diagram of a planar model of the continuously variable amplitude reciprocating drive mechanism according to an embodiment of the present invention;

[0072] Figure 6 This is a schematic diagram showing the fifth hinge point located at the bottom of the limiting groove, corresponding to the maximum amplitude of the slider, as described in this embodiment of the invention.

[0073] Figure 7 This is a schematic diagram showing the fifth hinge point of the present invention located at the uppermost end of the limiting groove, corresponding to the minimum amplitude of the slider.

[0074] Figure 8 This is a schematic diagram of the curve showing the relationship between the ordinate of the fifth hinge point and the amplitude of the slider in an embodiment of the present invention.

[0075] Figure 9 This is an exploded view of the main components of the fascia gun described in an embodiment of the present invention after disassembly.

[0076] Figure 10 This is an exploded view of the continuously variable amplitude reciprocating drive mechanism of the fascia gun and its surrounding components after disassembly, as described in an embodiment of the present invention.

[0077] Explanation of reference numerals in the attached figures:

[0078] 1-Upper shell; 2-Reciprocating drive mechanism; 3-Front cover; 4-Lower shell; 5-Handle; 6-Rear cover; 7-Connecting rod; 8-Bearing; 9-Output rod; 10-Slider; 101-Piston; 11-Adjusting rod; 12-Sliding block; 13-Threaded knob; 14-Fastening block; 15-Limiting groove; 16-Eccentric wheel; 17-Motor mounting bracket; 18-Motor. Detailed Implementation

[0079] The embodiments of the present invention will now be described in detail with reference to the accompanying drawings.

[0080] This invention aims to improve the design efficiency of continuously variable amplitude reciprocating drive mechanisms, providing a continuously variable amplitude reciprocating drive mechanism and its design method, as well as a fascia gun. The continuously variable amplitude reciprocating drive mechanism includes a crank-slider mechanism consisting of an eccentric wheel, an output rod, a connecting rod, and a slider, sequentially hinged together, and an adjusting rod. The hinge point between the connecting rod and the slider is the first hinge point, the hinge point between the output rod and the connecting rod is the second hinge point, and the hinge point between the output rod and the eccentric wheel is the third hinge point. The adjusting rod has a swing end and an adjusting end. The moving end is hinged to the output rod via a fourth hinge point. The hinge point of the adjusting end of the adjusting rod is the fifth hinge point. The position of the fifth hinge point is adjustable, and after adjustment, it limits the swing range of the second hinge point. The method includes: determining the functional relationship between the first distance between the first hinge point and the second hinge point, the second distance between the second hinge point and the third hinge point, the third distance between the third hinge point and the fourth hinge point, and the position of the fifth hinge point and the slider amplitude, and designing a continuously variable reciprocating drive mechanism based on the functional relationship.

[0081] In the continuously variable amplitude reciprocating drive mechanism, the slider is rotatably connected to one end of the connecting rod via a first hinge point, the other end of the connecting rod is rotatably connected to one end of the output rod via a second hinge point, the middle of the output rod is rotatably connected to the eccentric wheel via a third hinge point, the other end of the output rod is rotatably connected to the swing end of the adjusting rod via a fourth hinge point, and the adjusting end of the adjusting rod is rotatably connected to the position adjustment mechanism via a fifth hinge point. Based on this structure, when the input end of the eccentric wheel rotates, the output rod oscillates back and forth with the rotation of the eccentric wheel. The connecting rod and the adjusting rod move with the swing of the output rod. When the adjusting end of the adjusting rod is in different positions, the swing amplitude and swing range of the second hinge point connecting the connecting rod and the output rod will change accordingly, and this change is transmitted to the slider through the connecting rod, thus altering the slider amplitude. In the aforementioned continuously variable amplitude reciprocating drive mechanism, the eccentricity of the eccentric wheel is basically fixed, and the slider amplitude mainly depends on the position and length of the output rod, connecting rod, and adjusting rod, but the change in slider amplitude is relatively complex. Based on this, the present invention determines the functional relationship between the first distance between the first and second hinge points, the second distance between the second and third hinge points, the third distance between the third and fourth hinge points, and the position of the fifth hinge point and the slider amplitude. Then, based on this functional relationship, the design of a continuously variable amplitude reciprocating drive mechanism is carried out. Specifically, the rotational connection position of the adjusting end of the adjusting rod and the lengths of the output rod and connecting rod that satisfy the functional relationship can be selected according to design requirements. Alternatively, the slider amplitude can be verified based on the functional relationship. This eliminates the need to establish a three-dimensional simulation model and repeatedly adjust the three-dimensional simulation model, simplifying the design operation and improving design efficiency.

[0082] Example

[0083] Please see Figures 1 to 3 The continuously variable reciprocating drive mechanism described in this embodiment includes a crank-slider mechanism consisting of an eccentric wheel 16, an output rod 9, a connecting rod 7, and a slider 10, which are sequentially hinged together, and an adjusting rod 11. The hinge point between the connecting rod 7 and the slider 10 is the first hinge point A, the hinge point between the output rod 9 and the connecting rod 7 is the second hinge point B, and the hinge point between the output rod 9 and the eccentric wheel 16 is the third hinge point C. The adjusting rod 11 has a swing end and an adjusting end. The swing end of the adjusting rod 11 is hinged to the output rod 9 through a fourth hinge point D, and the hinge point of the adjusting end of the adjusting rod 11 is the fifth hinge point E. The position of the fifth hinge point E is adjustable, and after adjustment, it limits the swing range of the second hinge point B.

[0084] In this embodiment, the adjusting end of the adjusting rod 11 is hinged to a position adjusting mechanism, which can be a limiting slide groove 15. The adjusting end of the adjusting rod 11 is hinged to a sliding block 12, which can be slidably disposed in the limiting slide groove 15. The sliding block 12 is provided with a slider fixing mechanism for fixing the sliding block 12 to the limiting slide groove 15. The slider fixing mechanism is a threaded knob 13 and a fastening block 14 that is threadedly engaged with the threaded knob 13. When the threaded knob 13 is tightened, the sliding block 12 is fixedly disposed on the limiting slide groove 15.

[0085] In the above-mentioned continuously variable reciprocating drive mechanism, when the input end of the eccentric wheel 16 rotates, the output rod 9 swings back and forth with the rotation of the eccentric wheel 16. The connecting rod 7 and the adjusting rod 11 move with the swing of the output rod 9. When the adjusting end of the adjusting rod 11, i.e. the fifth hinge point E, is in different positions, the swing amplitude and swing range of the second hinge point B where the connecting rod 7 and the output rod 9 are hinged will change accordingly, and will be transmitted to the slider 10 through the connecting rod 7, thereby changing the slider amplitude F.

[0086] Please see Figure 4 This embodiment provides a design method for a continuously variable amplitude reciprocating drive mechanism, which is used to design the aforementioned continuously variable amplitude reciprocating drive mechanism, and mainly includes the following steps:

[0087] Step 1: Determine the functional relationship between the first distance AB between the first hinge point A and the second hinge point B, the second distance BC between the second hinge point B and the third hinge point C, the third distance CD between the third hinge point C and the fourth hinge point D, and the position of the fifth hinge point E and the slider amplitude F.

[0088] It is understandable that in the aforementioned continuously variable amplitude reciprocating drive mechanism, the eccentricity of the eccentric wheel 16, i.e., the distance between the rotation input end of the eccentric wheel 16 and the third hinge point C, is basically fixed. Furthermore, when the first distance AB, the second distance BC, the third distance CD are fixed, and the position of the fifth hinge point E is fixed, the fifth distance DE between the fourth hinge point D and the fifth hinge point E must also be fixed. Therefore, the slider amplitude F mainly depends on the positions of the first distance AB, the second distance BC, the third distance CD, and the fifth hinge point E. Based on this, this embodiment creates a functional relationship between the positions of the first distance AB, the second distance BC, the third distance CD, and the fifth hinge point E and the slider amplitude F, and designs the continuously variable amplitude reciprocating drive mechanism based on this functional relationship. This eliminates the need to establish a three-dimensional simulation model and repeatedly adjust the three-dimensional simulation model, simplifying the design process and improving design efficiency.

[0089] In this embodiment, the method for determining the functional relationship specifically includes:

[0090] Step 11: Construct a planar model of the continuously variable amplitude reciprocating drive mechanism;

[0091] Step 12: In the planar model, establish a rectangular coordinate system with the rotation input end of the eccentric wheel as the origin O;

[0092] Please see Figure 5 In this embodiment, a planar model of the continuously variable amplitude reciprocating drive mechanism is constructed based on each hinge point and the line segments between each hinge point. Based on this planar model, the rotation input end of the eccentric wheel 16 is taken as the origin O, and the straight line containing the origin O and the first hinge point A is taken as the x-axis to establish a rectangular coordinate system. Of course, other straight lines can be chosen as the x-axis in practical applications, and this embodiment does not impose any restrictions on this.

[0093] Step 13: Based on the Cartesian coordinate system, determine the position coordinates (x, y) of the first distance AB, the second distance BC, the third distance CD, and the fifth hinge point E. E y E The functional relationship between the slider amplitude F and the slider amplitude F.

[0094] By constructing a planar model of the continuously variable reciprocating drive mechanism, a rectangular coordinate system is built in the planar model, and the functional relationship is determined based on the rectangular coordinate system. At the same time, the position of the rotational connection of the adjusting end of the adjusting rod 11, i.e. the position of the fifth hinge point E, is reflected by the coordinates in the rectangular coordinate system, thereby improving the efficiency and accuracy of determining the functional relationship.

[0095] In this embodiment, the steps for determining the functional relationship based on the rectangular coordinate system specifically include:

[0096] Step 131: Determine the left limit point C1 and the right limit point C2 when the third hinge point C rotates at the rotation input end of the eccentric wheel 16;

[0097] It is understandable that in the above continuously variable reciprocating drive mechanism, when the input end of the eccentric wheel 16 rotates, it will cause the position of the third hinge point C to change. The motion trajectory of the third hinge point C is a circle with the origin O as the center and the radius r as the eccentricity. When the third hinge point C is located at the left limit point C1, the slider 10 has the maximum distance relative to the third hinge point C. When the third hinge point C is located at the right limit point C2, the slider 10 has the minimum distance relative to the third hinge point C. The difference between the maximum distance and the minimum distance is the slider amplitude F.

[0098] Based on this, in the rectangular coordinate system constructed in this embodiment, the left limit point C1 and the right limit point C2 are located on the x-axis on both sides of the origin O. When determining the left limit point C1 and the right limit point C2 of the third hinge point C, they can be specifically determined by the eccentricity r of the eccentric wheel 16. The x-coordinate corresponding to the left limit point C1 is less than 0, which is the opposite of the eccentricity -r; the x-coordinate corresponding to the right limit point C2 is greater than 0, which is the eccentricity r. Furthermore, since both the left limit point C1 and the right limit point C2 are located on the x-axis, their y-coordinates are both 0, that is, the position coordinates of the left limit point C1 are (-r, 0), and the position coordinates of the right limit point C2 are (r, 0).

[0099] It should be noted that when choosing other straight lines as the x-axis to establish a rectangular coordinate system, the ordinates of the left limit point C1 and the right limit point C2 do not necessarily have to be 0, but the specific calculation methods are the same. The relevant technical solutions for other rectangular coordinate systems will not be elaborated here. In the rectangular coordinate system created in this embodiment, the ordinates of the left limit point C1 and the right limit point C2 are 0, which facilitates calculation.

[0100] Step 132: Determine the position coordinates (x, y) of the point passing through the first distance AB, the second distance BC, the third distance CD, and the fifth hinge point E. E y E ) and the position coordinates (x) of the third hinge point C C y C The first calculation formula for calculating the fourth distance AC between the first hinge point A and the third hinge point C;

[0101] In this embodiment, the method for determining the first calculation formula is as follows:

[0102] Step 1321: Determine and calculate the position coordinates (x, y) of the fourth hinge point D. D y D The fourth calculation formula;

[0103] In the aforementioned continuously variable reciprocating drive mechanism, after the fifth hinge point E is fixed, the fourth hinge point D moves in a circular trajectory with the fifth hinge point E as the center and the fifth distance DE as the radius. Since the fourth hinge point D is the intersection of the output rod 9 and the adjusting rod 11, and is also restricted by the adjusting rod 11, the fourth hinge point D can only be within the arc segment from DL to DH, and must be the intersection of the first circle and the second circle. The circle with the fifth hinge point E as the center and the fifth distance DE as the radius is the first circle, and the circle with the third hinge point C as the center and the second distance BC as the radius is the second circle. Based on this, this embodiment can obtain the fourth calculation formula through the system of equations formed by the equations of the first and second circles.

[0104] The equation of the first circle is as follows:

[0105] (x D -x E ) 2 +(y D -y E ) 2 =DE 2 ;

[0106] The equation of the second circle is as follows:

[0107] (x D -x C ) 2 +(y D -y C ) 2 =BC 2 .

[0108] It is understandable that if the first distance AB, the second distance BC, and the third distance CD are fixed, and the position of the fifth hinge point E is fixed, then the fifth distance DE between the fourth hinge point D and the fifth hinge point E must also be fixed. Therefore, in practical applications, the fifth distance (x, y, y) can be determined by the position coordinates (x, y, y) of the fifth hinge point E. E y E The fifth distance DE is determined by using the first distance AB, the second distance BC, and the third distance CD. Determining the circle equation in this way further improves the efficiency and accuracy of the fourth calculation formula.

[0109] Step 1322: Determine the position coordinates (x, y) of the point passing through the fourth hinge point D. D y D ) and the position coordinates (x) of the third hinge point C C y C The fifth formula for calculating the slope k of the straight line containing output rod 9;

[0110] It is understood that both the third hinge point C and the fourth hinge point D are located on the straight line where the output rod 9 is located. Therefore, in this embodiment, the slope k of the straight line where the output rod 9 is located can be calculated using the position coordinates of the third hinge point C and the fourth hinge point D. The specific formula is the fifth calculation formula, as follows:

[0111]

[0112] Step 1323: Determine the sixth calculation formula for calculating the fourth distance AC using the slope k, the first distance AB, and the second distance BC. Combine the fourth, fifth, and sixth calculation formulas to obtain the first calculation formula.

[0113] In triangle ABC formed by the first hinge point A, the second hinge point B, and the third hinge point C, the sum of all interior angles is 180 degrees. Therefore, using trigonometric theorems, the fourth distance AC can be calculated based on the first distance AB, the second distance BC, and the slope k of the line containing output rod 9. The specific formula is the sixth calculation formula, as follows:

[0114] in:

[0115] ∠B = 180° - ∠A - ∠C

[0116] In the formula, ∠A, ∠B, and ∠C are the interior angles of triangle ABC.

[0117] Step 133: Take the position coordinates of the left limit point C1 as the position coordinates of the third hinge point C and substitute them into the first calculation formula to obtain the maximum fourth distance AC. max The second calculation formula uses the position coordinates of the right limit point C2 as the position coordinates of the third hinge point C and substitutes them into the first calculation formula to obtain the minimum fourth distance AC. min The third calculation formula;

[0118] Specifically, the position coordinates (-r, 0) of the left limit point C1 are taken as the position coordinates (x, y) of the third hinge point C. C y C Substituting this into the first calculation formula, we obtain the maximum fourth distance AC. max The second calculation formula can be expressed by a system of equations as follows:

[0119]

[0120] In the formula, x D1 Let y be the x-coordinate of the fourth hinge point D when the third hinge point C is located at the left limit point C1. D1Let be the ordinate of the fourth hinge point D when the third hinge point C is located at the left limit point C1, k1 be the slope when the third hinge point C is located at the left limit point C1, and ∠A1, ∠B1, and ∠C1 be the interior angles of triangle ABC when the third hinge point C is located at the left limit point C1.

[0121] The position coordinates (r, 0) of the right limit point C2 are taken as the position coordinates (x, y) of the third hinge point C. C y C Substitute this into the first calculation formula to obtain the minimum fourth distance AC. min The third calculation formula can be expressed in the following form by a system of equations:

[0122]

[0123] In the formula, x D2 Let y be the x-coordinate of the fourth hinge point D when the third hinge point C is located at the right limit point C2. D2 Let be the ordinate of the fourth hinge point D when the third hinge point C is located at the right limit point C2, and k2 be the slope when the third hinge point C is located at the right limit point C2. ∠A2, ∠B2, and ∠C2 are the interior angles of triangle ABC when the third hinge point C is located at the right limit point C2.

[0124] Step 134: Subtract the second calculation formula from the third calculation formula to obtain the functional relationship, that is:

[0125] F = AC max -AC min .

[0126] By determining the first calculation formula for the fourth distance AC in the rectangular coordinate system, and substituting the position coordinates of the left limit point C1 and the right limit point C2 into the first calculation formula and taking the difference, the calculation formula for the slider amplitude F can be obtained. This calculation formula can be used as the above functional relationship, thus further improving the efficiency and accuracy of determining the functional relationship.

[0127] In this embodiment, the axis of the second hinge point B of the continuously variable reciprocating drive mechanism can be coaxial with the axis of the fourth hinge point D. That is, the second hinge point B and the fourth hinge point D can be located on the same axis. In this case, in the planar model, the second hinge point B and the fourth hinge point D coincide, and their position coordinates in the Cartesian coordinate system are the same. In this case, the same method described above can be used to determine the functional relationship. In practical applications, the second hinge point B and the fourth hinge point D can be interchanged. For example, in the fifth calculation formula, the slope k of the straight line where the output rod 9 is located can be calculated using the position coordinates of the third hinge point C and the second hinge point B. The specific determination methods for both are the same, and will not be repeated in this embodiment.

[0128] Step 2: Design the continuously variable amplitude reciprocating drive mechanism based on the aforementioned functional relationship.

[0129] After obtaining the above functional relationship, the continuously variable reciprocating drive mechanism can be designed using this functional relationship, specifically as follows:

[0130] The determined coordinates (x, y) of the first distance AB, the second distance BC, the third distance CD, and the fifth hinge point E are used to define the coordinates of the points. E y E Substitute the given function relationship to calculate the slider amplitude F, and determine whether the slider amplitude F meets the design requirements.

[0131] In practical applications, the coordinates (x, y) of the first distance AB, the second distance BC, the third distance CD, and the fifth hinge point E can be used as a reference. E y E The amplitude F of the slider is verified to determine whether it meets the design requirements, thereby improving design efficiency.

[0132] For example, assuming AB = 42, BC = CD = 13, r = 2.5, and the position coordinates of E are (38.9, -16), the corresponding slider amplitude F can be calculated based on the above functional relationship. The specific process is as follows:

[0133] 1. Using the equation of the first circle (x) D -x E ) 2 +(y D -y E ) 2 =DE 2 The equation of the second circle (x) D -x C ) 2 +(y D -y C ) 2 =BC 2 The position coordinates of D are calculated as follows:

[0134] When C is located at C1, D is located at D1. The position coordinates of C1 are (-r, 0), and the position coordinates of D1 are (8.0, -7.65).

[0135] When C is located at C2, D is located at D2. The position coordinates of C2 are (r, 0), and the position coordinates of D2 are (7.13, -12.14).

[0136] 2. Using the coordinates of point D and point C, calculate the slope of the line containing the output rod:

[0137] When C is located at C1, k1 = (-7.65 - 0) / (8 + 2.5) = 0.72;

[0138] When C is located at C2, k2 = (-12.14 - 0) / (7.13 - 2.5) = 2.6.

[0139] 3. Through formula The included angle ∠C between AC and BC in triangle ABC is calculated as follows:

[0140] When C is located at C1, ∠C1 = 36 degrees;

[0141] When C is located at C2, ∠C2 = 69 degrees.

[0142] 4. Based on the trigonometric theorem, using formulas The angle ∠A between AB and AC is calculated as follows:

[0143] When C is located at C1, ∠A1 = 10 degrees;

[0144] When C is located at C2, ∠A2 = 16 degrees.

[0145] 5. Based on the fact that the sum of the interior angles of a triangle is 180 degrees, the included angle ∠B between AB and BC can be calculated using the formula ∠B = 180° - ∠A - ∠C:

[0146] When C is located at C1, ∠B1 = 133 degrees;

[0147] When C is located at C2, ∠B2 = 94 degrees.

[0148] 6. Based on the trigonometric theorem, using formulas AC is calculated as follows:

[0149] When C is located at C1, AC max =54.3;

[0150] When C is located at C2, AC min =42.3.

[0151] Therefore, the slider amplitude of the above mechanism is F = 54.3 - 42.3 = 12.

[0152] Therefore, the calculated slider amplitude F can be used to determine whether the current reciprocating drive mechanism meets the design requirements, thus verifying the slider amplitude F.

[0153] Please see Figures 6 to 8 In the continuously variable reciprocating drive mechanism of this embodiment, assuming that the first distance AB, the second distance BC, and the third distance CD are all fixed, the position adjustment mechanism limits the position of the adjustment end of the adjustment rod 11, i.e., the fifth hinge point E, within the limiting slide groove 15. This will cause the x-coordinate of the fifth hinge point E to be... EAssuming the first distance AB, the second distance BC, and the third distance CD are all fixed, then based on the above functional relationship, the ordinate y of the fifth hinge point E within the limiting groove 15 can be obtained. E The curve showing the variation between the slider amplitude F and the fifth hinge point E is shown. This curve indicates that the slider amplitude reaches its maximum value when the fifth hinge point E is at the bottom of the limiting groove 15, and its minimum value when the fifth hinge point E is at the top of the limiting groove 15. In practical use, the vertical position of the adjusting end of the adjusting rod 11 within the limiting groove 15 can be adjusted based on this curve to ensure that the slider amplitude F meets the requirements.

[0154] This embodiment designs a continuously variable amplitude reciprocating drive mechanism based on the aforementioned functional relationship, and may further include:

[0155] Based on the slider amplitude F determined according to the design requirements and the aforementioned functional relationship, adjust the positions of the first distance AB, the second distance BC, the third distance CD, and / or the fifth hinge point E.

[0156] In practical applications, the lengths of the connecting rod 7 and the output rod 9 can be adjusted based on functional relationships to achieve adjustments to the first distance AB, the second distance BC, and the third distance CD. The position of the fifth hinge point E can also be adjusted to make the continuously variable reciprocating drive mechanism achieve the slider amplitude F required by the design, thereby improving design efficiency.

[0157] In this embodiment, the following conditions should be met when adjusting the position of the fifth hinge point E:

[0158] |DE-BC1|<CE<|DE+BC1|;

[0159] |DE-BC2|<CE<|DE+BC2|;

[0160] In the formula, DE is the fifth distance between the fourth hinge point D and the fifth hinge point E, CE is the sixth distance between the third hinge point C and the fifth hinge point E, BC1 is the seventh distance between the second hinge point B and the left limit point C1, and BC2 is the eighth distance between the second hinge point B and the right limit point C2.

[0161] The above conditions enable the output rod 9 and the adjusting rod 11 to have an intersection point, thereby allowing the output rod 9 and the adjusting rod 11 to be rotatably connected through the fourth hinge point D, which can further improve design efficiency.

[0162] This embodiment designs a continuously variable amplitude reciprocating drive mechanism based on the aforementioned functional relationship, and may further include:

[0163] Based on the design requirements, the range of change of slider amplitude F, the first distance AB, the second distance BC, and the third distance CD, and based on the functional relationship, multiple positions of the fifth hinge point E are determined, and a position adjustment mechanism for the fifth hinge point E is designed based on the multiple positions of the fifth hinge point E.

[0164] In practical applications, it may be necessary to adjust the slider amplitude F. In this embodiment, multiple positions of the fifth hinge point E can be determined based on the adjustment range of the slider amplitude F and the functional relationship. The corresponding position adjustment mechanism can be designed by the trajectory formed by the multiple positions of the fifth hinge point E, so that the slider amplitude F is exactly within the design adjustment range under the adjustment of the position adjustment mechanism, thus improving the accuracy of the design.

[0165] Please see Figures 9 to 10 The aforementioned continuously variable amplitude reciprocating drive mechanism can be applied to fascia gun products. The fascia gun includes a mounting cavity composed of a lower shell 4, an upper shell 1, a front cover 3, and a rear cover 6. The continuously variable amplitude reciprocating drive mechanism 2 is installed in the mounting cavity. The slider 10 is a piston 101. The fascia gun may also include a motor 18 for driving the eccentric wheel 16 to rotate. The piston 101 is slidably disposed in the piston hole of the front cover 3. The rotation input end of the eccentric wheel 16 is fixedly connected to the output shaft of the motor 18. The motor 18 is disposed on the motor fixing bracket 17.

[0166] In practical applications, the space occupied by the continuously variable amplitude reciprocating drive mechanism can be evaluated based on the size of the fascia gun housing. Based on the evaluation results and functional relationships, the corresponding sizes of the connecting rod and output rod, as well as the positions of the corresponding hinge points, can be selected, thereby further improving design efficiency.

[0167] In summary, the continuously variable amplitude reciprocating drive mechanism and its design method, as well as the fascia gun provided in this embodiment, establish a functional relationship between the first distance AB, the second distance BC, the third distance CD, the position of the fifth hinge point E, and the slider amplitude F. When designing the aforementioned continuously variable amplitude reciprocating drive mechanism, the rotational connection position of the adjusting end of the adjusting rod 11, as well as the lengths of the output rod 9 and the connecting rod 7, can be selected according to design requirements based on this functional relationship. Alternatively, the slider amplitude F can be verified based on the functional relationship, eliminating the need to establish a three-dimensional simulation model and repeatedly adjust it, thus simplifying the design operation and improving design efficiency. By creating a rectangular coordinate system in the planar model of the continuously variable amplitude reciprocating drive mechanism and establishing a functional relationship within that system, the efficiency and accuracy of determining the functional relationship are improved. In practical applications, the required slider amplitude F may be a range. This embodiment can also determine multiple positions of the fifth hinge point E corresponding to this range based on the functional relationship, and then design the position adjustment mechanism for the fifth hinge point E, thereby improving the accuracy of the design.

Claims

1. A design method for a continuously variable amplitude reciprocating drive mechanism, characterized in that, The continuously variable reciprocating drive mechanism includes a crank-slider mechanism consisting of an eccentric wheel, an output rod, a connecting rod, and a slider, which are sequentially hinged together, as well as an adjusting rod. The hinge point between the connecting rod and the slider is the first hinge point, the hinge point between the output rod and the connecting rod is the second hinge point, and the hinge point between the output rod and the eccentric wheel is the third hinge point. The adjusting rod has a swing end and an adjusting end. The swing end of the adjusting rod is hinged to the output rod through a fourth hinge point, and the hinge point of the adjusting end of the adjusting rod is the fifth hinge point. The position of the fifth hinge point is adjustable, and after adjustment, it limits the swing range of the second hinge point. The method includes: determining a first distance between the first hinge point and the second hinge point, a second distance between the second hinge point and the third hinge point, a third distance between the third hinge point and the fourth hinge point, and the position of the fifth hinge point; determining the functional relationship between the first distance, the second distance, the third distance, and the position coordinates of the fifth hinge point and the slider amplitude; and designing a continuously variable amplitude reciprocating drive mechanism based on the functional relationship, specifically including: Substitute the determined first distance, second distance, third distance, and fifth hinge point position coordinates into the function relationship to calculate the slider amplitude and determine whether the slider amplitude meets the design requirements. The methods for determining the functional relationship include: Construct a planar model of the continuously variable amplitude reciprocating drive mechanism; In the planar model, a rectangular coordinate system is established with the rotation input end of the eccentric wheel as the origin; Based on the Cartesian coordinate system, determine the functional relationship between the position coordinates of the first distance, the second distance, the third distance, and the fifth hinge point and the slider amplitude; The method for determining the functional relationship specifically includes: Determine the left and right limit points of the third hinge point when it rotates at the rotation input end of the eccentric wheel; A first calculation formula is used to calculate the fourth distance between the first hinge point and the third hinge point by determining the first distance, the second distance, the third distance, the position coordinates of the fifth hinge point and the position coordinates of the third hinge point; The second calculation formula for the maximum fourth distance is obtained by substituting the coordinates of the left limit point as the coordinates of the third hinge point into the first calculation formula, and the third calculation formula for the minimum fourth distance is obtained by substituting the coordinates of the right limit point as the coordinates of the third hinge point into the first calculation formula. The function relationship is obtained by subtracting the second calculation formula from the third calculation formula.

2. The design method of the continuously variable reciprocating drive mechanism as described in claim 1, characterized in that, The method for determining the first calculation formula is as follows: Determine the fourth calculation formula for calculating the position coordinates of the fourth hinge point; A fifth calculation formula is used to calculate the slope of the straight line containing the output rod by using the position coordinates of the fourth hinge point and the position coordinates of the third hinge point; A sixth calculation formula for calculating the fourth distance using the slope, the first distance, and the second distance is determined. The fourth, fifth, and sixth calculation formulas are then combined to obtain the first calculation formula.

3. The design method of the continuously variable amplitude reciprocating drive mechanism as described in claim 2, characterized in that, The method for determining the fourth calculation formula is as follows: The equation of the first circle is determined with the center of the fifth hinge point and the radius of the fifth distance, where the fifth distance is the distance between the fourth hinge point and the fifth hinge point; Determine the equation of the second circle with the center at the third hinge point and the radius at the second distance; The system of equations formed by the first and second circle equations is used as the fourth calculation formula.

4. The design method of the continuously variable reciprocating drive mechanism as described in claim 3, characterized in that, The equation of the first circle is as follows: ； The equation of the second circle is as follows: ； In the formula, Let x be the x-coordinate of the fourth hinge point. Let be the ordinate of the fourth hinge point. Let x be the x-coordinate of the fifth hinge point. Let be the ordinate of the fifth hinge point. Let x be the x-coordinate of the third hinge point. Let y be the ordinate of the third hinge point, DE be the fifth distance, and BC be the second distance.

5. The design method of the continuously variable reciprocating drive mechanism as described in claim 2, characterized in that, The fifth calculation formula is as follows: ； The sixth calculation formula is as follows: ,in: ， ， ； In the formula, k is the slope. Let x be the x-coordinate of the fourth hinge point. Let be the ordinate of the fourth hinge point. Let x be the x-coordinate of the third hinge point. Let be the ordinate of the third hinge point, AC be the fourth distance, AB be the first distance, and BC be the second distance. , , These are the interior angles of the triangle formed by the first hinge point, the second hinge point, and the third hinge point, respectively.

6. The design method of the continuously variable reciprocating drive mechanism as described in claim 1, characterized in that, The design of the continuously variable amplitude reciprocating drive mechanism based on the aforementioned functional relationship also includes: Based on the slider amplitude determined according to the design requirements and the aforementioned functional relationship, adjust the positions of the first distance, the second distance, the third distance, and / or the fifth hinge point.

7. The design method of the continuously variable reciprocating drive mechanism as described in claim 6, characterized in that, The position of the fifth hinge point must at least satisfy the following conditions: ； ； In the formula, CE is the sixth distance between the third hinge point and the fifth hinge point, DE is the fifth distance between the fourth hinge point and the fifth hinge point, BC1 is the seventh distance between the second hinge point and the left limit point, and BC2 is the eighth distance between the second hinge point and the right limit point.

8. The design method of the continuously variable reciprocating drive mechanism as described in claim 1, characterized in that, The design of the continuously variable amplitude reciprocating drive mechanism based on the aforementioned functional relationship also includes: Based on the determined range of slider amplitude variation, first distance, second distance, and third distance according to the design requirements and based on the functional relationship, multiple positions of the fifth hinge point are determined, and a position adjustment mechanism for the fifth hinge point is designed according to the multiple positions of the fifth hinge point.

9. The design method of the continuously variable reciprocating drive mechanism as described in any one of claims 1 to 8, characterized in that, The axis of the second hinge point is coaxial with the axis of the fourth hinge point.

10. A continuously variable amplitude reciprocating drive mechanism, characterized in that, The device includes a crank-slider mechanism consisting of an eccentric wheel, an output rod, a connecting rod, and a slider, which are sequentially hinged together, as well as an adjusting rod. The hinge point between the connecting rod and the slider is the first hinge point, the hinge point between the output rod and the connecting rod is the second hinge point, and the hinge point between the output rod and the eccentric wheel is the third hinge point. The adjusting rod has a swing end and an adjusting end. The swing end of the adjusting rod is hinged to the output rod through a fourth hinge point, and the hinge point of the adjusting end of the adjusting rod is the fifth hinge point. The position of the fifth hinge point is adjustable, and after adjustment, it limits the swing range of the second hinge point. The continuously variable amplitude reciprocating drive mechanism is designed using the design method for continuously variable amplitude reciprocating drive mechanisms as described in any one of claims 1 to 9.

11. The continuously variable amplitude reciprocating drive mechanism as described in claim 10, characterized in that, It also includes a position adjustment mechanism, wherein the adjustment end of the adjustment rod is hinged to the position adjustment mechanism, and the position adjustment mechanism drives the adjustment end of the adjustment rod to move relative to the position.

12. A fascia gun, comprising a mounting cavity formed by a lower shell, an upper shell, a front cover, and a rear cover, and a motor, characterized in that, The fascia gun further includes a continuously variable reciprocating drive mechanism as described in any one of claims 10 to 11, wherein the slider is a piston, the piston is slidably disposed in the piston hole of the front cover, and the rotation input end of the eccentric wheel is fixedly connected to the output shaft of the motor.

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