Continuously variable amplitude reciprocating drive mechanism and fascia gun with the reciprocating drive mechanism

Abstract

The present invention relates to the field of fascia guns, and in particular to a continuously variable amplitude reciprocating drive mechanism with a simple and reliable structure. The mechanism includes a slider-crank mechanism consisting of a crank, an output rod, a connecting rod, and a slider which are hinged in sequence, and further includes a swing adjustment mechanism, where the hinge point between the output rod and the connecting rod is a swing hinge point, and the swing adjustment mechanism is configured to adjust and define the swing range of the swing hinge point. According to the present invention, when the amplitude of the piston is adjusted, the eccentric distance of the eccentric wheel does not change. Therefore, the key to adjust the amplitude of the piston is to adjust the swing amplitude of the swing hinge point of the output rod. The present invention is particularly suitable for being widely used in fascia gun products.

Description

Technical Field

[0001] The present invention relates to the field of percussion massagers, and particularly to a reciprocating drive mechanism with continuously variable amplitude and a percussion massager with such a reciprocating drive mechanism.

Background Art

[0002] A percussion massager, also known as a deep fascia impactor, is a soft tissue massage device used to relax the soft tissues of the human body by means of high-frequency impacts. Existing percussion massagers drive a massage head to perform a linear reciprocating motion via a piston. The massage head comes into contact with the human body and generates high-frequency vibrations acting on the deep muscles, thereby reducing the tension of local tissues, relieving pain, and promoting blood circulation. Existing percussion massagers have achieved the function of adjusting the amplitude of the massage head, whereby users can select an appropriate amplitude depth of the percussion massager for massage physiotherapy according to their own conditions. For example, professional athletes need to use a percussion massager with a deep amplitude depth to relax their muscles after exercise. General consumers, especially beginners, need to first use a percussion massager with a shallow amplitude depth and then gradually use a percussion massager with a deep amplitude depth as needed.

[0003] In existing fascia guns with adjustable amplitude depth, the adjustment principle involves designing a mechanism that allows for direct adjustment of the eccentricity distance, and then adjusting the vibration amplitude of the piston by adjusting the distance between the motor's output shaft and the eccentric wheel's output shaft. Taking Patent Document 1 as an example, this solution relates to the field of massage devices, and more particularly to a fascia gun with variable amplitude, in which case the amplitude of the fascia gun can be achieved by switching between forward and reverse rotation states of the motor. The fascia gun includes a motor, an eccentric distance adjustment member with an eccentric shaft, a connecting rod, and a piston rod. One end of the connecting rod is rotatably connected to the eccentric shaft, and the other end of the connecting rod is rotatably connected to the piston rod. The eccentric distance adjustment member includes a sliding skew block and an eccentric slider structure with an eccentric shaft. The motor's output shaft is screw-connected to the sliding skew block. The sliding skew block slides on the eccentric slider structure under the motor's drive, pressing against the eccentric slider structure and moving perpendicular to the motor's output shaft. In this solution, the eccentric distance is directly adjusted by changing the position of the sliding skew block to adjust the piston amplitude. However, this adjustment method requires the eccentric distance to be adjusted directly, the structure is relatively complex, and stability cannot be ensured after the amplitude is adjusted. [Prior art documents] [Patent Documents]

[0004] [Patent Document 1] Chinese Patent Application Publication No. 115444733 Specification [Overview of the Initiative]

[0005] The technical problem to be solved by the present invention is to provide a reciprocating drive mechanism with a simple and reliable structure for continuous variable amplitude, and a fascia gun with the reciprocating drive mechanism.

[0006] To solve the technical problems, the present invention employs a technical solution in which a continuously variable amplitude reciprocating drive mechanism comprises a slider-crank mechanism consisting of a sequentially hinged crank, output rod, connecting rod, and slider, and a swing adjustment mechanism, wherein the hinge point between the output rod and the connecting rod is the swing hinge point, and the swing adjustment mechanism is configured to adjust and define the swing range of the swing hinge point. When the mechanism is actually in motion, the output rod swings back and forth with the rotation of the crank, and the output rod drives the connecting rod and then drives the slider to move back and forth. In this case, the reciprocating swing amplitude and swing range of the hinge point between the output rod and the connecting rod (i.e., the swing hinge point) are adjusted, and once the reciprocating swing amplitude and swing range of the adjusted swing hinge point are defined, a new reciprocating amplitude of the slider can be obtained to adjust the amplitude of the slider. In this solution, the reciprocating amplitude of the slider is continuously adjusted by such a simple yet sophisticated structural design. Compared to existing continuous adjustment methods, such continuous adjustment effectively reduces structural complexity and manufacturing costs, and can help users perform the adjustments.

[0007] A preferred structural configuration for the oscillation adjustment mechanism is the following solution: The oscillation adjustment mechanism includes an adjustment rod having an oscillation end and an adjustment end, the oscillation end of the adjustment rod being hinged to an output rod, and the hinged position of the adjustment end of the adjustment rod being adjustable. In actual use, the oscillation end of the adjustment rod is rotatably connected to the output rod, so that the adjustment rod moves in conjunction with the oscillation of the output rod. When it is necessary to adjust the amplitude of the slider, the rotatable connection position of the adjustment end of the adjustment rod is adjusted to change the oscillation range of the oscillation hinge point, and the amplitude of the slider is adjusted accordingly. This solution features a simple structural design while effectively achieving the effect of adjusting the amplitude of the slider.

[0008] In actual applications, the above structure can be selected as the following specific structural configuration: namely, the crank is an eccentric wheel, the connecting rod is a rocking arm, the slider is a piston, the connection line between the rotational connecting ends of the output rod and rocking arm and the rotational input end of the eccentric wheel is a first cycloid, the connection line between the adjustment end of the adjustment rod and the rotational input end of the eccentric wheel is a second cycloid, the angle between the first cycloid and the reciprocating axis of the piston is the first angle θ, the angle between the second cycloid and the reciprocating axis of the piston is the second angle β, and the second angle β is adjusted so that the oscillation range of the first angle θ is adjusted in a chain reaction. The second angle β is adjusted to change the oscillation trajectory of the output rod, which inevitably leads to a change in the oscillation range of the oscillation hinge point of the output rod, further achieving adjustment of the piston amplitude. The first cycloid corresponds to the connecting line od in Figure 16, the second cycloid corresponds to the connecting line og in Figure 16, and the horizontal line in Figure 16 is the piston reciprocating axis. In the above structure, the reciprocating amplitude of the piston satisfies the following relationship, namely F = L1 * |Cosθmax - Cosθmin|, where F represents the reciprocating amplitude of the piston, L1 represents the length of the first cycloid, θmax represents the maximum oscillation angle of the first cycloid with respect to the second angle β, and θmin represents the minimum oscillation angle of the first cycloid with respect to the second angle β. Preferably, the second angle β is in the range of -20° to 30°, and the oscillation angle of the first angle θ is in the range of -20° to 90°. To prevent rotational failure due to jamming, the value of θ does not include 90°. With the above structure, the chain reaction of changes in the oscillation range of the first angle θ caused by adjusting the second angle β can be accurately calculated, and as a result, the reciprocating amplitude can be calculated. This provides a structural basis for implementing a continuously variable amplitude reciprocating drive mechanism in a specific product, allowing for precise control of the continuous amplitude adjustment process.

[0009] To simplify the structure and achieve smooth transmission, the present invention can employ a solution in which the output hinge point between the output rod and the crank, the adjustment hinge point between the output rod and the oscillating end of the adjustment rod, and a projection plane perpendicular to the rotational input end of the eccentric wheel, wherein the output hinge point, adjustment hinge point, and oscillating hinge point are all projected onto the projection plane to obtain corresponding projection points, and the narrow angle of the connection line between any two projection points is in the range of 0° to 360°. In actual design, the shape of the output rod is diverse. The structure of the output rod defined by the above projection relationship may be a rod extending along a straight line, a bent rod, or a disc, etc. In addition to planar structures, three-dimensional structures with convex or concave structures at any hinge point can also be used as output rods if the above projection relationship is satisfied. On the other hand, the adjustment hinge point between the output rod and the oscillating end of the adjustment rod may also extend in two opposite directions from the oscillating hinge point. However, regardless of the specific shape, as long as the narrow angle of the connection line between the projections of any two hinge points is within the range of 0°-360°, the formed operating mechanism can be ensured to realize the transmission of corresponding oscillating and reciprocating motions, and the reciprocating amplitude can be adjusted. The narrow angle of the connection line does not include the two endpoint values ​​of 0° and 360°.

[0010] To adjust the position of the adjustment end of the adjustment rod in real time, a position adjustment mechanism can be selected. The adjustment end of the adjustment rod is hinged to the position adjustment mechanism, which drives the adjustment end of the adjustment rod to move relative to a certain position. The position of the adjustment end of the adjustment rod can be conveniently and reliably adjusted via the position adjustment mechanism, thereby driving the adjustment rod to adjust the swing range of the swing hinge point of the output rod, and adjusting the amplitude of the slider.

[0011] In a specific embodiment of the position adjustment mechanism, the mechanism includes a lead screw and a lead screw nut, the lead screw nut being rotatably positioned at the adjustment end of an adjustment rod, the lead screw being connected to a drive unit, the drive unit rotationally driving the lead screw, thereby driving the lead screw nut to slide axially along the lead screw. Specifically, the drive unit rotationally drives the lead screw and then drives the lead screw nut to slide along the extending direction of the lead screw, thereby changing the position of the adjustment end of the adjustment rod. This not only makes the entire adjustment process very convenient and accurate, but also provides a structural basis for subsequent commercialization. Preferably, the drive unit is a drive motor or a manual knob to achieve a more rational drive mode, optimize product costs, and support product diversification.

[0012] In another specific embodiment of the position adjustment mechanism, the position adjustment mechanism may be a limit chute, where the adjustment end of an adjustment rod is hinged to a slider slidably positioned within the limit chute, and a slider fixing mechanism is provided on the slider for fixing the slider to the limit chute, the slider fixing mechanism comprising a threaded knob and a fastening block that screws into the threaded knob, the slider being positioned and fixed on the limit chute when the threaded knob is tightened. The slider is restricted to sliding within the limit chute, and the position of the adjustment end of the adjustment rod is also adjusted in the slider sliding process. If it is necessary to fix the slider to a specified position within the limit chute, only the threaded knob needs to be tightened, and the position of the slider can be fixed so that the slider is positioned and fixed within the limit chute via the threaded knob, thereby obtaining the required amplitude range of the piston.

[0013] Another preferred structural configuration of the oscillation adjustment mechanism includes a limit baffle, where the oscillation range of the oscillation hinge point is set within the oscillation range of the limit baffle, and the oscillation range of the limit baffle is adjustable. The limit baffle forms a relative oscillation range, and the entire operating trajectory of the oscillation hinge point is restricted to the oscillation range. If necessary, the oscillation range of the limit baffle alone can be adjusted to obtain a new oscillation range of the oscillation hinge point and adjust the amplitude of the slider.

[0014] In a more preferred embodiment of the above solution, preferably, the limit baffle has two baffles, the oscillating hinge point is positioned between the two baffles, and the distance between the two baffles is adjustable. The two baffles form a relative oscillating range, restricting the oscillating hinge point to move within the oscillating range. If necessary, the oscillating range of the oscillating hinge point can be adjusted simply by adjusting the distance between the two baffles or the positions of the two baffles, and then the amplitude of the slider can be adjusted. In this solution, the positions of the baffles are flexibly positioned according to the actual placement needs, thereby saving the corresponding placement space. Furthermore, the oscillating range of the limit baffle is directly adjusted to obtain a large oscillating adjustment range for the oscillating hinge point, and further to obtain a large amplitude adjustment range for the slider.

[0015] A corresponding fascia gun can also be obtained based on a continuously variable amplitude reciprocating drive mechanism. The fascia gun comprises a mounting chamber consisting of a lower shell, an upper shell, a front cover, and a rear cover, and a motor for rotationally driving a crank, with the slider being a piston slidably positioned in the piston hole of the front cover. In actual use, if the user needs to adjust the vibration amplitude of the piston of the fascia gun, only the oscillation adjustment mechanism can be easily adjusted to conveniently adjust the oscillation amplitude and oscillation range of the output rod, thereby achieving the adjustment needs. The fascia gun obtained based on the above continuously variable amplitude reciprocating drive mechanism has a significantly simplified amplitude adjustment system structure, is easy to implement at the product level, and will become widely adopted in later stages. In addition, this structure also allows the user to adjust the amplitude more conveniently and accurately, thereby greatly improving the user experience.

[0016] As a further optimization of the above solution, preferably the crank is an eccentric wheel, and the rotational input end of the eccentric wheel is connected and fixed to the output shaft of the motor. The eccentric wheel of the fascia gun is combined with the motor of the fascia gun, and if the eccentric distance of the eccentric wheel is not adjusted, the amplitude of the piston can be adjusted via a reciprocating drive mechanism with continuously variable amplitude.

[0017] To facilitate the mounting and fixing of the oscillation adjustment mechanism, a motor fixing stand can be optionally added, and the motor and oscillation adjustment mechanism are placed on the motor fixing stand. As a mechanism for adjusting the oscillation amplitude and oscillation range of the output rod, the oscillation adjustment mechanism is subjected to high-frequency reaction forces during the actual operating process. Therefore, the stability of the position of the oscillation adjustment mechanism is a design point that needs to be considered in the actual product. Considering the limited internal placement space of the fascia gun product, the oscillation adjustment mechanism is placed on the motor fixing stand, thereby making good use of the stand originally used to fix the motor, further saving placement space, and making the internal layout more rational. To achieve the above stable placement, mounting holes can be provided in the oscillation adjustment mechanism, and the oscillation adjustment mechanism is placed on the motor fixing stand via the mounting holes.

[0018] The present invention has the beneficial effect of enabling existing fascia guns to achieve adjustable amplitude by directly adjusting the eccentricity distance of the fascia gun, that is, by increasing or decreasing the eccentricity distance. However, achieving this structural design in actual products is difficult. Adjustable eccentricity distance leads to problems such as increased wear and vibration of related components, decreased overall structural stability, and high product production and manufacturing costs. On the other hand, it is necessary to adjust the relative position by changing the eccentricity distance between the oscillating arm and the eccentric wheel, and if the relative position changes during operation, the stability of the mechanism subjected to amplitude adjustment cannot be guaranteed, making it difficult to guarantee the stability of the mechanism subjected to amplitude adjustment during actual use.

[0019] According to the present invention, when the piston amplitude is adjusted, the eccentricity distance of the eccentric wheel does not change. Therefore, the key to adjusting the piston amplitude is to adjust the oscillation amplitude of the oscillation hinge point of the output rod. Specifically, as the eccentric wheel rotates, the output rod oscillates back and forth, and changes in the oscillation amplitude and oscillation range of the oscillation hinge point of the output rod are transmitted to the piston via the oscillation arm, which ultimately leads to a change in the reciprocating amplitude of the piston. A further oscillation adjustment mechanism is configured to directly control and adjust the oscillation range of the oscillation hinge point in order to directly and effectively adjust the reciprocating trajectory of the piston. Because the oscillation amplitude and oscillation range of the oscillation hinge point are adjusted, internal relative connections do not cause changes in relative position during the adjustment process, resulting in better operational stability of the mechanism subjected to amplitude adjustment. The present invention is particularly suitable for widespread use in fascia gun products. [Brief explanation of the drawing]

[0020] [Figure 1] This is a schematic diagram illustrating the mechanical operation of a continuously variable amplitude reciprocating drive mechanism. [Figure 2] This is a schematic diagram showing the adjustment of the oscillation range of the oscillation hinge point d of a reciprocating drive mechanism with continuously variable amplitude via an adjustment rod. [Figure 3]It is a schematic diagram showing the definition of the swing range of the swing hinge point d of the reciprocating drive mechanism with continuously variable amplitude by the upper and lower buffers. [Figure 4] It is a schematic diagram showing the maximum amplitude range of the corresponding piston when the adjustment rod of the present invention is arranged at the lower end of the limit shoot. [Figure 5] It is a schematic diagram showing the minimum amplitude range of the corresponding piston when the adjustment rod of the present invention is arranged at the upper end of the limit shoot. [Figure 6] It is a schematic diagram showing the piston at the maximum stroke position when the adjustment rod of the present invention is arranged at the position where the piston has the maximum amplitude range. [Figure 7] It is a schematic diagram showing the piston at the minimum stroke position when the adjustment rod of the present invention is arranged at the position where the piston has the maximum amplitude range. [Figure 8] It is a schematic diagram showing the piston at the maximum stroke position when the adjustment rod of the present invention is arranged at the position where the piston has the minimum amplitude range. [Figure 9] It is a schematic diagram showing the piston at the minimum stroke position when the adjustment rod of the present invention is arranged at the position where the piston has the minimum amplitude range. [Figure 10] It is a schematic diagram showing the piston at the maximum stroke position when the adjustment rod of the present invention is arranged at the position where the amplitude range of the piston is between the maximum amplitude range and the minimum amplitude range. [[ID=X]] [Figure 11] It is a schematic diagram showing the piston at the minimum stroke position when the adjustment rod of the present invention is arranged at the position where the amplitude range of the piston is between the maximum amplitude range and the minimum amplitude range. [Figure 12] It is a schematic diagram showing that the adjustment rod of the present invention is arranged at one of the swing limit positions. [Figure 13] It is a schematic diagram showing that the adjustment rod in FIG. 12 is swung to another swing limit position. [Figure 14] It is a schematic diagram of the piston amplitude calculation method. [Figure 15]This is a schematic diagram showing that the position adjustment mechanism for a continuously variable amplitude reciprocating drive mechanism consists of a lead screw and a lead screw nut. [Figure 16] This is a schematic diagram showing the relationship between the adjustment angles of a continuously variable amplitude reciprocating drive mechanism in one embodiment. [Figure 17] This is an exploded view showing the main components of the fascial cancer according to the present invention. [Figure 18] This is an exploded view showing the continuously variable amplitude reciprocating drive mechanism and surrounding components according to the present invention. [Figure 19] This is a schematic structural diagram showing one embodiment of a continuously variable amplitude reciprocating drive mechanism according to the present invention. [Figure 20] This is a schematic structural diagram showing the limit chute of the continuously variable amplitude reciprocating drive mechanism according to the present invention. [Modes for carrying out the invention]

[0021] The symbols are as follows: Upper shell 1, reciprocating drive mechanism 2, front cover 3, lower shell 4, handle 5, rear cover 6, connecting rod 7, bearing 8, output rod 9, crank 91, limit baffle 92, slider 10, piston 101, adjustment rod 11, slider 12, threaded knob 13, fastening block 14, limit chute 15, eccentric wheel 16, motor fixing stand 17, motor 18, slider position for minimum piston amplitude range 111, maximum piston The slider position 112 of the amplitude range, the third slider position 113, the first limit oscillation position f1 of the output rod, the second limit oscillation position f2 of the output rod, the piston amplitude range f, the power supply a, the output hinge point c, the oscillation hinge point d, the adjustment hinge point e, the rotation point g between the adjustment rod and the slider, the lead screw 151, the lead screw nut 152, the drive unit 153, the first cycloid length L1, the first narrowing angle θ, the second narrowing angle β, the first spacing A, and the second spacing B.

[0022] Figures 1-3 illustrate the structure and control principle of a continuously variable amplitude reciprocating drive mechanism. Figure 1 shows a slider-crank mechanism consisting of a crank 91, output rod 9, connecting rod 7, and slider 10, which are sequentially hinge-coupled. Figure 3 is a schematic diagram showing a limit baffle 92 additionally provided at the oscillating hinge point d. The oscillation range of the oscillating hinge point d is within the oscillation range of the limit baffle 92. Figure 2 is a schematic diagram of the output rod 9, which is the connecting rod. Taking Figure 2 as an example, the output rod 9 oscillates while its rotation is transmitted to the output hinge point c via the rotational power source a. However, the right end of the oscillating output rod 9 is constrained by the adjustment rod 11, and its oscillation amplitude and oscillation range are inevitably different from those in the normal state. The left end of the output rod 9 is rotatably connected to the connecting rod 7, which moves while the output rod 9 oscillates to reciprocate the slider 10. During adjustment, the right end of the adjustment rod 11 (i.e., the relative position of the rotation point g between the adjustment rod and the slider) slides, specifically, the adjustment rod 11 and the adjustment hinge point e allow the oscillation trajectory of the output rod 9 to be adjusted, thereby adjusting the oscillation amplitude of the oscillation hinge point d, and further adjusting the amplitude of the slider 10. In this configuration, if the eccentricity distance is not adjusted, the oscillation amplitude and its oscillation range of the output rod 9 are adjusted, the related adjustment structure is clearly optimized, and mass production of the product is facilitated. Furthermore, this adjustment mode can also be applied during the use of the fascia gun, thereby greatly improving the convenience of use and user experience.

[0023] After a continuously variable amplitude reciprocating drive mechanism is applied to a specific myofascial gun product, a schematic diagram of the associated structure is shown in Figures 4 to 20. First, a mounting chamber is constructed from a lower shell 4, an upper shell 1, a front cover 3, and a rear cover 6. The reciprocating drive mechanism 2 is placed in the mounting chamber, and the piston 101 of the reciprocating drive mechanism 2 is slidably positioned in the piston hole of the front cover 3. As shown in Figure 18, the motor 18 transmits rotational power to the eccentric wheel 16 via an output shaft, thereby driving the eccentric wheel 16 to rotate. The rotating eccentric wheel 16 is rotatably connected to an output rod 9 via the output shaft of the eccentric wheel 1. The output rod 9 is rod-shaped, with one end of the output rod rotatably connected to a connecting rod 7, and the other end of the output rod rotatably connected to an adjustment rod 11. After the aforementioned infrastructure is connected, a specific structure as shown in Figure 19 is obtained. During actual movement, the eccentric wheel 16 rotates with the output shaft of the motor 18, and the rotating eccentric wheel 16 drives the output rod 9 to oscillate accordingly. The amplitude of the piston 101 is constant when the position of the slider 12 at the adjustment end of the adjustment rod 11 is fixed. When it is necessary to adjust the amplitude of the piston 101, the threaded knob 13 is loosened and the position of the slider 12 is adjusted. As the position of the slider 12 is changed, the adjustment rod 11 adjusts the oscillation state of the output rod 9 by adjusting the hinge point e, that is, the adjustment rod adjusts the oscillation range of the oscillation hinge point d, and then adjusts the amplitude of the piston 101.

[0024] Figures 6 to 11 are considered examples. When the right end of the adjustment rod 11 is in the position shown in Figure 6, that is, when the right end of the adjustment rod 11 is in the slider position 112, the piston 101 is within the maximum amplitude range. Figure 6 shows the piston 101 moved to its leftmost end, and the distance D1 between the left end of the piston 101 and the piston bush is 19.9 mm. Figure 7 shows the piston 101 moved to its rightmost end, and the distance D2 between the left end of the piston 101 and the piston bush is 6.8 mm. Therefore, the amplitude stroke of the piston 101 is 19.9 - 6.8 = 13.1 mm.

[0025] When the right end of the adjustment rod 11 is in the position shown in Figures 8 and 9, that is, when the right end of the adjustment rod 11 is in the slider position 111, the piston 101 is within the minimum amplitude range. Figure 8 shows the state where the piston 101 has moved to its leftmost end, and the distance D3 between the left end of the piston 101 and the piston bush is 26 mm. Figure 9 shows the state where the piston 101 has moved to its rightmost end, and the distance D4 between the left end of the piston 101 and the piston bush is 21.7 mm, and therefore the amplitude stroke of the piston 101 is 26 - 21.7 = 4.3 mm.

[0026] As shown in Figures 10 and 11, when the right end of the adjustment rod 11 is positioned between the two limit positions described above, that is, when the right end of the adjustment rod 11 is at the position 113 of the third slider, the amplitude range of the piston 101 is between the maximum and minimum ranges. Figure 10 shows the piston 101 moved to its leftmost end, where the distance D5 between the left end of the piston 101 and the piston bush is 26.3 mm. Figure 11 shows the piston 101 moved to its rightmost end, where the distance D6 between the left end of the piston 101 and the piston bush is 16 mm, and the amplitude stroke of the piston 101 is 26.3 - 16 = 10.3 mm.

[0027] According to the three positions described above, the amplitude stroke of the corresponding piston 101 can be adjusted within a range of 4.3 mm to 13.1 mm.

[0028] Furthermore, Figure 16 also shows in detail the relationship between angle adjustment and amplitude change in the above structure. In Figure 16, point O is the center of the motor shaft, rotation point g between the adjustment rod and the slider is the rotation center of the adjustment rod, adjustment hinge point e is the rotational connection point between the output rod and the adjustment rod, output hinge point c is the rotational connection point between the output rod and the eccentric wheel, oscillating hinge point d is the rotational connection point between the oscillating arm and the output rod, the angle between segment og and the horizontal axis is β, i.e., the second angle β, and the angle between segment od and the horizontal axis is θ, i.e., the first angle θ. As the motor rotates with the eccentric wheel, the oscillating arm is restricted by the adjustment rod, allowing it to perform planar motion, i.e., oscillate back and forth. When the second angle β is changed, the oscillating arm is driven to oscillate within the corresponding range of oscillation with the first angle θ, and the piston rod is driven to reciprocate within the corresponding amplitude F, which indicates that the amplitude F increases as the second angle β decreases. When the position of the rotation point g changes to correspond to the second angle β, the difference in projected distance between the oscillation limit positions of segment od in the horizontal direction is the current reciprocating distance F of the piston, and the angle between segment od and the horizontal direction in the reciprocating oscillation process changes in the range θmax~θmin, i.e., F=od*|Cosθmax-Cosθmin|, where od is L1. The amplitude F is adjusted by changing the position of the rotation point g (i.e., changing the position of the second angle β), which indicates that the amplitude F increases as the second angle β decreases, and the position of the rotation point g is continuously adjusted to achieve the corresponding continuous adjustment of the amplitude F. The amplitude F is adjusted within the range Fmax-Fmin. The second angle β is in the range of -20° to 30°, and the first angle θ is in the range of -20° to 90° (excluding 90°). The relationship between the second angle β, the first angle θ, and the amplitude F can be explained with reference to Figure 16, using the following list of experimental data. JPEG0007901173000001.jpg87136

[0029] As can be seen from the above test data and Figure 16, as the second clamping angle β gradually decreases in the range of 27° to -19°, the amplitude F gradually increases, and the adjustable range of amplitude is 11.95 - 4.61 = 7.34 mm. Furthermore, when the second clamping angle β is adjusted in the range of -19° to 27° using the adjustment rod 11, the adjustable range of piston amplitude is 7.34 mm, that is, the amplitude is changed and adjusted in the range of 4.61 mm to 11.95 mm.

[0030] In Figure 12, the distance between the output hinge point c and the oscillating hinge point d is the first distance A, and the distance between the output hinge point c and the adjustment hinge point e is the second distance B. As shown in Figure 13, when the output rod 9 is positioned at the second limit oscillating position f2, its axis is marked as f2. As shown in Figure 14, when the output rod 9 is at the first limit oscillating position f1, its axis is marked as f1. Positions f2 and f1 are projected onto the straight line along which the piston 10 reciprocates, and the difference in projected lengths obtained by the projection is marked as f, which is the amplitude f of the piston, i.e., the amplitude stroke described above. A schematic diagram of the corresponding projection is also marked in Figure 14.

[0031] Figure 15 shows the position adjustment mechanism consisting of a lead screw 151 and a lead screw nut 152. Compared to the adjustment method of the slider 12, the drive adjustment method of the lead screw 151 and lead screw nut 152 can achieve a better effect of electrically driven continuous adjustment, thereby making the amplitude adjustment of the piston 101 more accurate and convenient, and further promoting its use in fascia gun products. During actual use, the drive unit 153 rotates the lead screw 151, and relative rotation occurs between the rotating lead screw 151 and the lead screw nut 152 under the action of the threads between the lead screw and the lead screw nut 152. Such relative rotation drives the lead screw nut 152 to slide along the axial direction of the lead screw 151. The lead screw nut 152 is slidably mounted, and specifically, a guide sliding rod passing through the lead screw nut, or a chute structure that guides and restricts the sliding of the lead screw nut 152 can be employed, thereby changing the helical motion between the lead screw nut 152 and the drive lead screw 151 to the sliding of the lead screw nut 152, and adjusting the position of the adjustment end of the adjustment rod 11.

[0032] In actual design, the position and structural form of the position adjustment mechanism only need to be such that the adjustment end of the adjustment rod 11 can be driven to move relative to a certain position. Therefore, the position adjustment mechanism can be linear or curved. In addition, the positional relationship between the position adjustment mechanism and the output rod 9 is also based on the fact that the adjustment end of the adjustment rod 11 can be driven to move relative to a certain position.

Claims

1. A fascia gun comprising a slider-crank mechanism and a mounting chamber, The slider-crank mechanism is composed of a crank (91), an output rod (9), a connecting rod (7), and a slider (10) that are sequentially hinge-coupled, and is equipped with a swing adjustment mechanism, wherein the hinge point between the output rod (9) and the connecting rod (7) is the swing hinge point (d), and the swing adjustment mechanism is configured to adjust and define the swing range of the swing hinge point (d). The oscillation adjustment mechanism comprises an adjustment rod (11) having an oscillation end and an adjustment end, the oscillation end of the adjustment rod (11) being hinged to the output rod (9), and the hinged position of the adjustment end of the adjustment rod (11) being adjustable. The device further includes a position adjustment mechanism, wherein the adjustment end of the adjustment rod (11) is hinged to the position adjustment mechanism, and the position adjustment mechanism drives the adjustment end of the adjustment rod (11) to move to a certain position. The position adjustment mechanism comprises a lead screw (151) and a lead screw nut (152), the lead screw nut (152) being rotatably positioned on the adjustment end of the adjustment rod (11), the lead screw (151) being connected to a drive unit, and the drive unit (153) driving and rotating the lead screw (151) to drive the lead screw nut (152) to slide axially along the lead screw (151). The mounting chamber comprises a lower shell (4), an upper shell (1), a front cover (3), and a rear cover (6), and includes a motor (18) for rotationally driving a crank (91), the slider (10) being a piston (101) slidably positioned in a piston hole of the front cover (3), the crank (91) being an eccentric wheel (16), and the rotation input end of the eccentric wheel (16) being connected and fixed to the output shaft of the motor (18), in a fascia gun.

2. The fascia gun according to claim 1, further comprising a motor fixing stand (17), wherein the motor (18) and the oscillation adjustment mechanism are arranged on the motor fixing stand (17).

3. The fascia gun according to claim 1, wherein the crank (91) is an eccentric wheel (16), the connecting rod (7) is a rocking arm, the slider (10) is a piston (101), the connection line between the rotational connection end of the output rod (9) and the rocking arm and the rotational input end of the eccentric wheel (16) is a first cycloid, the connection line between the adjustment end of the adjustment rod and the rotational input end of the eccentric wheel is a second cycloid, the angle between the first cycloid and the reciprocating axis of the piston is a first angle θ, the angle between the second cycloid and the reciprocating axis of the piston is a second angle β, and the second angle β is adjusted so that the rocking range of the first angle θ is adjusted in a chain reaction.

4. The fascia gun according to claim 3, wherein the reciprocating amplitude of the piston (101) satisfies the following relationship: F ​​= L1 * |Cosθmax - Cosθmin|, where F represents the reciprocating amplitude of the piston, L1 represents the length of the first cycloid, θmax represents the maximum oscillation angle of the first cycloid with respect to the second narrow angle β, and θmin represents the minimum oscillation angle of the first cycloid with respect to the second narrow angle β.

5. The fascia cancer according to claim 4, wherein the second angle β is in the range of -20° to 30°, and the oscillation angle of the first angle θ is in the range of -20° to 90°.

6. The fascia gun according to claim 3, comprising an output hinge point (c) between the output rod (9) and the crank (91), an adjustment hinge point (e) between the output rod (9) and the oscillating end of the adjustment rod (11), and a projection plane perpendicular to the rotation input end of the eccentric wheel (16), wherein the output hinge point (c), the adjustment hinge point (e), and the oscillating hinge point (d) are all projected onto the projection plane to obtain corresponding projection points, and the narrow angle of the connection line between any two projection points is in the range of 0° to 360°.

7. The fascia gun according to claim 1, wherein the drive unit (153) is a drive motor or a manual knob.

8. The fascia gun according to claim 1, wherein the position adjustment mechanism is a limit chute (15), the adjustment end of the adjustment rod (11) is hinged to a slider (12) slidably disposed within the limit chute (15), a slider fixing mechanism for fixing the slider (12) to the limit chute (15) is disposed on the slider (12), the slider fixing mechanism comprises a threaded knob (13) and a fastening block (14) that screws into the threaded knob (13), and the slider (12) is positioned and fixed on the limit chute (15) when the threaded knob (13) is tightened.

9. The fascia gun according to claim 1, wherein the oscillation adjustment mechanism includes a limit baffle (92), the oscillation range of the oscillation hinge point (d) is set to be within the oscillation range of the limit baffle (92), and the oscillation range of the limit baffle (92) is adjustable.

10. The fascia gun according to claim 9, wherein the limit baffle (92) has two baffles, the swing hinge point (d) is positioned between the two baffles, and the distance between the two baffles is adjustable.

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