Linkage adjustment mechanism and sewing machine having the same

Abstract

The present invention relates to the field of sewing equipment, and in particular to a linkage adjustment mechanism and a sewing machine having the same. The linkage adjustment mechanism is used to drive a presser foot mechanism and a feed tooth frame in the sewing machine to move, and comprises a driving component, a presser foot lifting driving assembly and an adjusting driving assembly, wherein: the driving component is connected to a motion output end of a driving source and can rotate with the driving source; the driving component has a first area and a second area, the first area is used to form a follow-up cooperation with the presser foot lifting driving assembly to drive the presser foot mechanism to move; the second area is used to form a follow-up cooperation with the adjusting driving assembly to drive the feed tooth on the feed tooth frame to change the position, the linkage adjustment mechanism can simultaneously drive the feed tooth frame and the presser foot mechanism to move through a driving component, and compared with the form of driving the two mechanisms separately, the overall sewing volume with the linkage adjustment mechanism is smaller.

Description

Technical Field

[0001] The invention relates to the field of sewing equipment, in particular to a linkage adjustment mechanism and a sewing machine having the same. Background Art

[0002] The existing sewing machine structure often includes multiple motion mechanisms for realizing different functions, such as a cloth feeding mechanism, a presser foot mechanism, a thread trimming mechanism, a lubrication mechanism, etc. These mechanisms coordinate with each other to complete the complete sewing function of the sewing machine.

[0003] In the sewing machine structure, the main function of the cloth feeding mechanism is to continuously lift and pull the cloth on the needle plate through the reciprocating elliptical motion of the cloth feeding rack, so as to continuously drag the cloth to be processed to the machine head to complete the entire feeding process; and the main function of the presser foot mechanism is to cooperate with the cloth feeding rack to complete the dragging of the cloth during the feeding process, and to press the cloth during the sewing process to smoothly complete the sewing work, and to lift the presser foot after sewing is completed to add material. In the sewing machine structure disclosed in the related prior art, the lifting of the presser foot in the presser foot mechanism is generally driven by an electromagnet, while the driving and azimuth adjustment of the cloth feeding mechanism are driven by a separate stepping motor.

[0004] Although the above-mentioned form of driving the two mechanisms separately can make the sewing machine fully functional and the two mechanisms can basically cooperate correctly with appropriate electronic control detection means, the driving device and the transmission structure connected thereto occupy a large space, which easily causes the overall size of the sewing machine to be too large. Summary of the invention

[0005] Based on this, it is necessary to provide a linkage adjustment mechanism and a sewing machine having the same to address the above problems. The linkage adjustment mechanism can drive the feed tooth frame and the presser foot mechanism to move through a driving component. Compared with the form of driving the two mechanisms separately, the overall sewing volume with the linkage adjustment mechanism is smaller.

[0006] A first aspect of the present invention provides a linkage adjustment mechanism for driving a presser foot mechanism and a feed tooth frame in a sewing machine, wherein the linkage adjustment mechanism comprises a driving member, a presser foot lifting driving assembly and an adjustment driving assembly, wherein:

[0007] The driving member is connected to the motion output end of the driving source and can rotate with the driving source;

[0008] The driving member has a first area and a second area, the first area is used to form a follow-up cooperation with the presser foot lifting driving assembly to drive the presser foot mechanism to move; and,

[0009] The second area is used to form a follow-up cooperation with the adjustment drive assembly to drive the position of the feed tooth on the feed tooth bracket to change.

[0010] In this way, the driving component is driven by a driving source, and has a first area and a second area on it, wherein: the presser foot lifting driving assembly and the adjustment driving assembly are respectively cooperated with the first area and the second area. In this way, one driving source can simultaneously drive the presser foot lifting driving assembly and the adjustment driving assembly to move. Compared with the form of solely driving the presser foot lifting assembly by electromagnetic drive and the feed tooth frame adjustment by a stepper motor, the overall linkage adjustment mechanism has fewer parts and a more compact structure.

[0011] In one embodiment, the second area includes a non-lower supply area and a lower supply area, when the adjustment drive assembly cooperates with the non-lower supply area, the feed teeth on the feed tooth rack are maintained in a non-lower supply state; when the adjustment drive assembly cooperates with the lower supply area, the feed teeth on the feed tooth rack are switched to the lower supply state.

[0012] In one of the embodiments, the second region includes a gear adjustment area, and the adjustment drive assembly can cooperate with the gear adjustment area to drive the feed tooth frame to rotate to perform gear switching.

[0013] With such arrangement, due to the follow-up cooperation between the adjustment drive assembly and the second area, when the adjustment drive assembly cooperates with the gear adjustment area to drive the feed tooth rack to rotate, the angle of the feed teeth on the feed tooth rack can be adjusted to meet the sewing needs of fabrics of different thicknesses.

[0014] In one of the embodiments, the second area includes a non-lower supply area and a lower supply area, when the adjustment drive assembly cooperates with the non-lower supply area, the feed teeth on the feed tooth rack are maintained in a non-lower supply state; when the adjustment drive assembly cooperates with the lower supply area, the feed teeth on the feed tooth rack are switched to a lower supply state; along the direction in which the driving member rotates with the driving source, the non-lower supply area and the lower supply area are respectively located on both sides of the gear adjustment area.

[0015] In one of the embodiments, the second region further includes a transition zone, and the transition zone is connected between the gear adjustment zone and the lower supply zone.

[0016] In this way, by setting a transition zone between the gear adjustment zone and the lower supply zone, the rotation of the feed tooth frame can be effectively buffered and noise reduced.

[0017] In one of the embodiments, the first area includes at least two presser foot lifting areas corresponding to the non-lower supply area and the lower supply area respectively, and when the presser foot lifting driving assembly cooperates with the presser foot lifting areas, the presser foot mechanism can be switched to the presser foot lifting state by the presser foot lifting driving assembly as the driving member rotates.

[0018] In one of the embodiments, the first area also includes a press-down holding area, and the press-down holding area corresponds to the gear adjustment area. When the adjustment drive assembly cooperates with the gear adjustment area, the presser foot lifting drive assembly cooperates with the press-down holding area and keeps the presser foot pressed down.

[0019] In this arrangement, the gear adjustment area corresponds to the downward pressure holding area. In this way, when the adjustment drive assembly cooperates with the gear adjustment area to adjust the angle of the feed tooth on the feed tooth rack, the presser foot lifting drive assembly cooperates with the downward pressure holding area to make the presser foot lifting drive assembly maintain the downward pressure state of the presser foot.

[0020] In one of the embodiments, along the direction in which the driving member rotates with the driving source, the pressing and holding area is connected between two sections of the presser foot lifting area.

[0021] In one embodiment, the first area is configured as a continuously arranged cam profile, and / or the second area is configured as a continuously arranged cam profile.

[0022] A second aspect of the present invention provides a sewing machine, comprising the above-mentioned linkage adjustment mechanism. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 The schematic diagram of the structure of the sewing machine provided by the present invention after hiding the housing and part of the structure, showing a linkage adjustment mechanism and various mechanisms associated therewith in an embodiment;

[0024] Figure 2 for Figure 1 A structural diagram of the relevant structure of the cloth feeding mechanism in the structure shown in ;

[0025] Figure 3 for Figure 1 Schematic diagram of components related to the presser foot lifting in the linkage adjustment mechanism and their connection relationship with the presser foot mechanism;

[0026] Figure 4 for Figure 1 Schematic diagram of the components in the linkage adjustment mechanism related to the adjustment mechanism drive and their connection relationship with the eccentric shaft in the adjustment mechanism;

[0027] Figure 5 It is a schematic diagram of the exploded structure of the adjustment mechanism and the feed tooth frame;

[0028] Figure 6 for Figure 1 A schematic diagram of a partial structure of a linkage adjustment mechanism of an embodiment shown in FIG, in which structures such as a drive source and a bracket are omitted;

[0029] Figure 7 for Figure 1 A schematic diagram of the relative positional relationship between the driving member and the two rollers in the linkage adjustment mechanism of the embodiment shown in FIG. 1 , and the contour area division of the two cams in the driving member is also indicated in the figure;

[0030] Figure 8 The schematic diagram of the structure of the sewing machine provided by the present invention after hiding the housing and part of the structure, showing another embodiment of the linkage adjustment mechanism and various mechanisms associated therewith;

[0031] Fig. 9 for Figure 8 A schematic diagram of a partial structure of the linkage adjustment mechanism shown in FIG, in which structures such as the drive source and the bracket are omitted;

[0032] Fig.10 A first perspective view of a modified embodiment of a driving member;

[0033] Fig.11 for Fig.10 A second perspective view of the drive member shown in FIG.

[0034] Fig.12 The structural diagram of the sewing machine provided by the present invention after hiding the housing and part of the structure, the linkage adjustment mechanism and Figure 8 The linkage mechanism of the embodiment shown in the figure differs only in the driving member;

[0035] Fig.13 for Fig.12 A schematic diagram of a partial structure of the linkage adjustment mechanism shown in FIG, in which structures such as the drive source and the bracket are omitted;

[0036] Fig.14 is a structural diagram of another linkage adjustment mechanism, in which the linkage adjustment mechanism shown in the figure is Figure 1 The linkage mechanism of the embodiment shown in the figure differs only in the driving member;

[0037] Fig.15 for Fig.14 A schematic diagram of a partial structure of the linkage adjustment mechanism shown in FIG. , in which structures such as a driving source and a bracket are omitted, and the outline area division of the driving component is also indicated in the figure;

[0038] Fig.16a It is a schematic diagram of the principle when the cloth feeding tooth frame is in a normal working state;

[0039] Fig.16b It is a schematic diagram of the principle when the feed tooth frame is in the thick material working state;

[0040] Fig.16c It is a schematic diagram of the principle when the feed tooth frame is in the thin material working state.

[0041] 100. Linkage adjustment mechanism;

[0042] 11. Driving source;

[0043] 12, driving member; 121, first cam; 1211, first presser foot lifting area; 1212, second presser foot lifting area; 1213, pressing holding area; 122, second cam; 123, slide groove;

[0044] 13. Presser foot lifting driving assembly; 131. Presser foot lifting crank; 1311. First rotary center piece; 132. Presser foot lifting roller; 133. Pull rod; 134. Presser foot lifting swing rod; 135. First elastic retaining piece;

[0045] 14. Adjustment drive assembly; 141. First adjustment connecting rod; 1411. Second rotation center piece; 142. Second adjustment connecting rod; 143. Adjustment crank; 144. Adjustment roller; 145. Second elastic retaining member; 146. Select connection member;

[0046] 15. Bracket;

[0047] 200, presser foot mechanism; 21, presser foot shaft; 22, presser foot arm; 23, presser foot plate;

[0048] 300. Adjustment mechanism;

[0049] 31. eccentric shaft; 310. concentric section; 311. eccentric section; 32. adjusting slider; 33. first retaining ring; 34. second retaining ring;

[0050] 400, cloth feeding mechanism; 41, first transmission assembly; 42, second transmission assembly; 43, third transmission assembly; 44, cloth feeding tooth frame; 441, active tooth frame; 4411, active tooth; 442, differential tooth frame; 4421, differential tooth; 443, extension arm; 444, adjustment slide;

[0051] 500, spindle; 600, needle plate. DETAILED DESCRIPTION

[0052] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0053] It should be noted that when a component is referred to as being "mounted on" another component, it may be directly mounted on the other component or there may be a central component. When a component is considered to be "set on" another component, it may be directly set on the other component or there may be a central component at the same time. When a component is considered to be "fixed to" another component, it may be directly fixed on the other component or there may be a central component at the same time.

[0054] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as those commonly understood by those skilled in the art to which the present invention belongs. The terms used herein in the specification of the present invention are only for the purpose of describing specific embodiments and are not intended to limit the present invention. The term "or / and" used herein includes any and all combinations of one or more of the related listed items.

[0055] refer to Figure 1 and Figure 2 As shown in , a sewing machine of an embodiment of the present invention includes a main shaft 500, which is connected to an external driving source (such as a rotating driving source such as a motor) and can rotate under the drive of the external driving source. The sewing machine can also include a presser mechanism 200, an adjustment mechanism 300, a cloth feeding mechanism 400, a needle plate 600 and a machine head (the machine head is hidden in the figure), wherein: the cloth feeding mechanism 400 and the machine head are connected to the main shaft 500, and can complete a preset action under the drive of the main shaft 500. The cloth feeding mechanism 400 is used to transport the cloth to be sewn to an appropriate position on the needle plate 600; the presser mechanism 200 is used to press the cloth delivered by the cloth feeding mechanism 400; the machine head is used to sew the cloth delivered by the cloth feeding mechanism 400.

[0056] Of course, in addition to the mechanisms mentioned above, the sewing machine may also include other mechanisms, such as a thread passing mechanism, a lubrication mechanism, a thread cutting mechanism, a material piercing mechanism, a thread hooking mechanism, a material cutting mechanism, etc. Multiple mechanisms coordinate with each other to realize the complete functions of the sewing machine.

[0057] The cloth feeding mechanism 400 includes a first transmission assembly 41, a second transmission assembly 42, a third transmission assembly 43 and a cloth feeding tooth frame 44, wherein the cloth feeding tooth frame 44 includes an active tooth frame 441 and a differential tooth frame 442; the first transmission assembly 41 is connected to the corresponding shaft section of the main shaft 500, and is used to drive the cloth feeding tooth frame 44 (including the active tooth frame 441 and the differential tooth frame 442) to move along the main shaft 500. Figure 1 The movement of the second transmission assembly 42 comes from the first transmission assembly 41, and can drive the differential rack 442 along the Z-axis direction under the input of the movement. Figure 1 The movement of the third transmission assembly 43 comes from the second transmission assembly 42, and can drive the active tooth frame 441 along the Y-axis direction under the input of the movement Figure 1 Reciprocating motion in the indicated Y-axis direction.

[0058] It can be understood that in the illustrated embodiment, the Z-axis direction is the vertical direction, or the direction perpendicular to the upper surface of the needle plate 600; the Y-axis direction is the horizontal direction, or the direction along which all the feed teeth on the feed tooth frame 44 are arranged. In other embodiments, the two directions can also be redesigned according to actual needs.

[0059] The active tooth frame 441 and the differential tooth frame 442 in the feed tooth frame 44 both move along the Z-axis direction and along the Y-axis direction at the same time. Therefore, the movements in the two directions are combined to make the feed tooth frame 44 perform reciprocating circular motion in the plane determined by the Y-axis and the Z-axis. In particular, in the present embodiment, the movement amplitude of the feed tooth frame 44 along the Y-axis direction is greater than the movement amplitude along the Z-axis direction. Therefore, the feed tooth frame 44 performs reciprocating elliptical motion in the plane determined by the Y-axis and the Z-axis. The elliptical motion enables the feed tooth frame 44 to drag the cloth in the Y-axis direction, thereby realizing the function of feeding cloth.

[0060] The active tooth frame 441 and the differential tooth frame 442 move synchronously along the Z-axis direction, and are driven by the third transmission assembly 43 and the second transmission assembly 42 respectively along the Y-axis to allow differential movement, which can be used to achieve a better sewing effect for the sewing machine.

[0061] In existing sewing machines, the cloth feed mechanism is generally designed for the processing requirements of a certain specific thickness of cloth. When the thickness of the cloth differs from the specific thickness, the cloth feed rack may not have enough drag force on the cloth or the single cloth feed amount may be too large during the sewing process, which may cause the cloth to be layered / the stitches to be too dense, or the cloth to be wrinkled. In order to enable the sewing machine to better adapt to the sewing operation of fabrics of different thicknesses, the sewing machine can also be configured with an adjusting mechanism 300, which can adjust the inclination angle of the feed tooth rack 44 according to the thickness of the fabric, thereby changing the inclination angle of the feed teeth on the feed tooth rack 44 (the feed teeth are tooth-like structures protruding on the feed tooth rack 44, and when the inclination angle of the feed tooth rack 44 changes, the inclination angle of the feed teeth relative to the upper surface of the needle plate 600 changes accordingly). At the same time, the tilting rotation of the feed tooth rack 44 also causes the height of the upper end of the feed teeth exceeding the upper surface of the needle plate 600 to change, and the feed teeth adapt to fabrics of different thicknesses by changing their own height and inclination angle.

[0062] refer to Figure 2 As shown in the figure, the end of the feed tooth frame 44 away from the needle plate 600 is provided with an extension arm 443, and the active tooth frame 441 and the differential tooth frame 442 are both provided with two extension arms 443 spaced apart from each other. In this way, a space is formed between the upper and lower groups of extension arms 443 along the length direction (or Figure 2 An adjustment slot 444 extending in the Y-axis direction (in the Y-axis direction indicated in FIG), the adjustment slot 444 is used to set the adjustment mechanism 300.

[0063] refer to Figure 1 and Figure 5 As shown in the figure, the adjustment mechanism 300 includes an eccentric shaft 31, an adjustment slider 32, a first retaining ring 33 and a second retaining ring 34, wherein: the eccentric shaft 31 includes a concentric segment 310 and an eccentric segment 311, and the motion for driving the adjustment mechanism 300 to move can be input from the concentric segment 310 to the eccentric shaft 31, so that the eccentric shaft 31 rotates around the concentric segment 310; the adjustment slider 32 is correspondingly arranged at Figure 2 The adjusting slider 32 is arranged in the adjusting slot 444 shown in the figure and can slide in the adjusting slot 444 . The adjusting slider 32 is installed on the eccentric section 311 of the eccentric shaft 31 .

[0064] When the eccentric shaft 31 rotates, the adjusting slider 32 can move in two directions at the same time: sliding along the adjusting slide groove 444, and moving in a direction perpendicular to the sliding direction to bias the feed tooth frame 44. The latter movement causes the extension arm 443 (indicated at Figure 2 One end of the feed tooth frame 44 is lifted or lowered, so that the feed tooth frame 44 as a whole rotates at a certain angle around the rotation connection between the feed tooth frame 44 and the main shaft 500.

[0065] refer to Figure 2As shown in FIG. 5 , since the active tooth frame 441 and the differential tooth frame 442 have different lengths extending along the Y-axis direction, the active teeth 4411 on the active tooth frame 441 and the differential teeth 4421 on the differential tooth frame 442 are arranged in a front-to-back spacing along the Y-axis direction. A notch (not marked in the figure) is provided on the needle plate 600 for accommodating the active teeth 4411 and the differential teeth 4421 to extend out. Further in combination with FIG. 5 , when the end of the feed tooth frame 44 away from the feed tooth setting (i.e., the adjustment slide 444) is lifted up or pressed down by the adjustment slider 32, the height of the active teeth 4411 and the differential teeth 4421 exposed from the upper surface of the needle plate 600 and the inclination angle of the teeth are also different, thereby forming an effect of adapting to the sewing of fabrics of different thicknesses. The "change of the feed tooth position" referred to in the present invention includes the height of the active teeth 4411 and the differential teeth 4421 exposed from the upper surface of the needle plate 600 and the inclination angle of the teeth.

[0066] Specifically, refer to Figures 16a to 16c As shown, Fig.16a Schematic diagram of the principle when the cloth feeding tooth frame 44 is in a normal working state. Fig.16b It is a schematic diagram of the principle when the cloth feeding tooth frame 44 is in the thick material working state. Fig.16c Schematic diagram of the principle of the cloth feeding tooth frame 44 in the thin material working state. In the figure, the sign S represents the elliptical motion trajectory of the active tooth 4411 and the differential tooth 4421, V represents the cutting angle direction when the active tooth 4411 and the differential tooth 4421 cut out the upper surface of the needle plate 600, and F represents the elastic force direction of the active tooth 4411 and the differential tooth 4421 on the cloth.

[0067] (1) When the feed tooth frame 44 is in the normal working state: the feed tooth frame 44 is neither lifted nor pressed down, but remains in a horizontal state. At this time, the active tooth 4411 and the differential tooth 4421 are also kept horizontal and flush, and the active tooth 4411 and the differential tooth 4421 contact the cloth synchronously. Therefore, the direction of the elastic force F exerted by the active tooth 4411 and the differential tooth 4421 on the cloth is the same as the cutting angle direction when the active tooth 4411 and the differential tooth 4421 cut out the upper surface of the needle plate 600, both of which are in the vertical direction. This state is suitable for sewing cloth of ordinary thickness and moderate hardness.

[0068] (2) When the feed tooth frame 44 is in the thick material working state: Figure 5 As shown in FIG. 1 , when it is necessary to adapt to the thick material working condition, the feed tooth frame 44 needs to be rotated to an inclined state. By adjusting the slider 32 to lift the feed tooth frame 44 away from the end where the feed tooth is set (i.e. Figure 2The adjusting groove 444 marked in the middle makes the feed tooth frame 44 tilted, so that the height of the active tooth 4411 is lower than the height of the differential tooth 4421 (when the swing angle is the same, since the active tooth 4411 is closer to the swing center of the feed tooth frame 44, its height moving below the needle plate 600 is smaller than the differential tooth 4421 which is relatively far away from the swing center of the feed tooth frame 44). At this time, the direction of the elastic force F acting on the cloth by the active tooth 4411 and the differential tooth 4421 remains in the vertical direction, but the cutting angle direction when the active tooth 4411 and the differential tooth 4421 cut out of the working plane no longer remains in the vertical direction, but the cloth is fed in an oblique cutting manner;

[0069] Since the height of the active teeth 4411 is lower than that of the differential teeth 4421, the differential teeth 4421 rises above the needle plate 600 before the active teeth 4411 and contacts the cloth in advance, and the cloth feeding efficiency of the differential teeth 4421 is higher than that of the active teeth 4411. Therefore, when the active teeth 4411 and the differential teeth 4421 are conveying cloth, the differential teeth 4421 has a certain catching-up effect relative to the active teeth 4411, forming a pushing effect on the cloth, so that thick materials such as multi-layers and stem seams can be fed smoothly, the stitch length is uniform, and the sewing quality is better.

[0070] (3) When the cloth feeding tooth frame 44 is in the thin material working state: similarly, still combined Figure 5 As shown in FIG. 1 , when it is necessary to adapt to the working condition of mesh or similar thin materials, the feed tooth frame 44 needs to be rotated in the opposite direction to the previous working condition to an inclined state. At this time, the feed tooth frame 44 is pressed down by adjusting the slider 32 to move away from the end of the feed tooth setting (i.e. Figure 2 The adjusting groove 444 marked in the middle makes the cloth feeding tooth frame 44 tilted, so that the height of the active tooth 4411 is higher than that of the differential tooth 4421. At this time, the direction of the elastic force F exerted on the cloth by the active tooth 4411 and the differential tooth 4421 remains in the vertical direction, but the cutting angle direction when the active tooth 4411 and the differential tooth 4421 cut out the upper surface of the needle plate 600 no longer remains in the vertical direction, and the active tooth 4411 and the differential tooth 4421 feed the cloth in an oblique cutting manner;

[0071] Since the height of the active tooth 4411 is higher than that of the differential tooth 4421, the active tooth 4411 rises above the needle plate 600 before the differential tooth 4421 and contacts the cloth in advance. The cloth feeding efficiency of the active tooth 4411 is higher than that of the differential tooth 4421. Therefore, when the active tooth 4411 and the differential tooth 4421 are conveying cloth, the active tooth 4411 has a certain distance effect relative to the differential tooth 4421, forming a dragging effect on the cloth, making thin materials such as mesh smooth and wrinkle-free, and the sewing quality is better.

[0072] Figures 16a to 16cThe three states of the feed tooth frame 44 shown in the figure correspond to the three gears of the feed tooth frame, wherein: the position of the feed tooth frame corresponding to the thin material working condition is called the first gear position of the feed tooth frame; the position of the feed tooth frame corresponding to the normal working condition is called the second gear position of the feed tooth frame; the position of the feed tooth frame corresponding to the thick material working condition is called the third gear position of the feed tooth frame. The switching process of the sewing machine between the three states is called the three-gear adjustment process of the feed tooth frame, or the gear adjustment of the feed tooth frame. In other embodiments, the feed tooth frame can also have more subdivided gears, that is, the selectable gears are more than the above three gears, but the adjustment principle is roughly the same as above, which will not be repeated here.

[0073] In addition, when placing fabric on the needle plate 600, or in some other necessary occasions, the feed tooth frame 44 needs to be deflected to a state where the active teeth 4411 and the differential teeth 4421 basically fall back below the needle plate 600, which is hereinafter referred to as the lower feeding state. The gear adjustment and lower feeding of the feed tooth frame 44 are both achieved by biasing the feed tooth frame 44 to rotate it, thereby driving the position change of the feed teeth thereon.

[0074] Continue to refer Figure 1 As shown in , the presser mechanism 200 includes a presser shaft 21, a presser arm 22 and a presser plate 23, wherein: the presser shaft 21 can rotate around its own axis, thereby driving the presser arm 22 to lift up or swing down, and then press the presser plate 23 to the upper surface of the needle plate 600, or lift the presser plate 23 away from the needle plate 600. It can be understood that the action of lifting the presser plate 23 away from the needle plate 600 by the presser shaft 21 and the presser arm 22 is hereinafter referred to as the presser foot lifting action, and the corresponding state of the presser plate 23 being lifted is called the presser foot lifting state. Correspondingly, the state of the presser plate 23 leaning against the needle plate 600 is called the pressing state.

[0075] Before sewing begins, the fabric to be sewn needs to be placed on the needle plate 600. At this time, the feed tooth rack 44 needs to be switched to the lower supply state so that the fabric can be placed above the needle plate. In the middle of sewing, there are often some occasions where material needs to be added. For example, when sewing a trademark on the fabric, it is necessary to pause the sewing process, place the trademark on the fabric on the needle plate 600, and then continue sewing. In this occasion of adding material in the middle, the presser foot needs to be lifted so that the trademark and the like can be placed under the presser foot 23 and at the appropriate position on the fabric on the needle plate 600. But at the same time, the feed tooth rack 44 needs to keep the feed teeth in contact with the fabric during this process of adding material in the middle, that is, the feed tooth rack does not lower. Otherwise, when the presser foot mechanism 200 is in the presser foot raising state, the feed tooth rack 44 switches to the lower feeding state. Then, when the material adding is finished and sewing is continued, the feed teeth on the feed tooth rack 44 extend out of the upper surface of the needle plate 600 again, which will slightly push the fabric. The subsequent sewing will cause the stitches on the fabric to change, greatly reducing the aesthetics of the sewn fabric.

[0076] In other words, the sewing machine needs to have the following three working states: (1) the presser foot is raised while feeding downward to meet the need of unloading the material; (2) the presser foot is raised while feeding downward to meet the need of adding material midway, so as to avoid the displacement of the fabric caused by the feed dog contacting the fabric again after a short period of non-contact before and after stopping, thus affecting the subsequent sewing effect; (3) the feed dog rack 44 can be adjusted between multiple gears so that the distance between the feed dog and the presser foot plate 23 and the angle of the feed dog can adapt to different fabric thicknesses, and the presser foot mechanism 200 remains in the downward state during the gear adjustment process.

[0077] In order to make the sewing machine obtain the above three working states, the most direct way is to drive them separately through independent drives. For example: in the applicant's own prior application, the presser foot lifting action is generally driven by an electromagnet; and the state switching method of the feed tooth frame, the applicant has proposed two methods: the first is to use a stepper motor to drive the eccentric shaft to drive the feed tooth frame to rotate to an inclined state or reset, to achieve a normal working state (moderate fabric thickness) and a thick material working state; on this basis, the applicant found that when it is suitable for sewing thin materials, the feed tooth frame can also be driven in reverse to rotate. Therefore, the detection and electrical control of the rotation angle of the eccentric shaft are added to this later scheme to achieve the gear adjustment of the feed tooth frame.

[0078] Although the single drive form can make the sewing machine obtain the above three working states, the driving device and the transmission structure connected thereto occupy a large space, which easily causes the overall size of the sewing machine to be too large. Therefore, the applicant has proposed a scheme to realize the presser foot lifting action and the lowering action at the same time. In this scheme, the lever for lifting the presser foot and the downward driving crank for driving the tooth frame to swing are respectively connected to the same presser foot lifting wrench through the first hook and the second hook. In this way, when the presser foot lifting wrench rotates, the presser foot lifting and the tooth frame can be driven to swing and realize the lowering action through the first hook and the second hook.

[0079] However, it was found during specific use that: since the first hook and the second hook are connected to the same presser foot lifter, in order to meet the travel requirements of the presser foot lifter, the swing travel of the presser foot lifter is preset. Therefore, in this structure, the tooth frame can only have two working conditions, namely, the reset state and the lower feeding state, and it is impossible to achieve gear adjustment to adapt to different fabric thicknesses. At the same time, generally speaking, when the swing lower feeding of the tooth frame and the presser foot lifting action are driven by the same structure, there is a linkage relationship between the tooth frame and the presser foot, that is, the movement of the presser foot lifter will inevitably cause the presser foot and the feed tooth frame to perform preset actions at the same time. However, in the aforementioned midway feeding condition, it is necessary to achieve the presser foot lifting while keeping the feed tooth frame from lowering, that is, at this time, the presser foot needs to move while the feed tooth frame does not lower, and this requirement contradicts the way in which the same drive structure drives the two to be linked. Therefore, in previous sewing machines, it is impossible to obtain the above three working states at the same time through one drive structure.

[0080] In order to resolve this contradiction, the present invention first provides a linkage adjustment mechanism 100, which can enable the sewing machine to have the above three working states simultaneously.

[0081] Reference Figure 1 and Figures 3 to 7 As shown in the figure, the linkage adjustment mechanism 100 includes a driving source 11, a driving member 12 connected to the motion output end of the driving source 11, a presser foot lifting driving assembly 13 for driving the presser foot shaft 21 in the presser foot mechanism 200 to rotate, and an adjustment driving assembly 14 for driving the eccentric shaft 31 in the adjustment mechanism 300 to rotate.

[0082] In the illustrated embodiment, the driving source 11 is mounted on the bracket 15, and the rotation axis s1 of the driving member 12 is also fixed relative to the bracket 15. The driving member 12 includes a relatively fixed first cam 121 and a second cam 122, which are used to drive the presser foot lifting driving assembly 13 and the adjusting driving assembly 14 respectively.

[0083] refer to Figure 1 and Figure 3 As shown in the figure, the first cam 121 drives the presser foot lifting drive assembly 13 to move. Referring to the position shown in the figure, the driving member 12 can be at the driving source (marked at Figure 1 The presser foot lifting driving assembly 13 comprises a presser foot lifting crank 131, a presser foot lifting roller 132, a pull rod 133 and a presser foot lifting swing rod 134. The presser foot lifting crank 131, the pull rod 133 and the presser foot lifting swing rod 134 are all roughly rod-shaped structures, wherein:

[0084] The presser foot lifter crank 131 has a first rotating center piece 1311 for rotationally connecting to the bracket 15, and the presser foot lifter crank 131 can rotate around the first rotating center piece 1311; the presser foot lifter roller 132 is rotationally connected to one end of the presser foot lifter crank 131 which is relatively far away from the first rotating center piece 1311, and the presser foot lifter roller 132 can maintain contact with the outer contour of the first cam 121, so that a cam mechanism is formed between the first cam 121 and the presser foot lifter crank 131 and the presser foot lifter roller 132, in which the first cam 121 is an active part and the presser foot lifter crank 131 is a driven part, and the contact between the two is realized through the presser foot lifter roller 132.

[0085] One end of the presser foot lifting swing rod 134 is connected to the presser foot shaft 21 in the presser foot mechanism 200, and this end of the presser foot lifting swing rod 134 can drive the presser foot shaft 21 to move along the presser foot mechanism 200. Figure 3 The pull rod 133 is connected between the presser foot lifting swing rod 134 and the presser foot lifting crank 131 to transmit motion between the two rods. In order to maintain reliable contact between the presser foot lifting roller 132 and the outer contour of the first cam 121, in the illustrated embodiment, the presser foot lifting drive assembly 13 also includes a first elastic retainer 135, which is configured as a torsion spring and is used to lift up one end of the presser foot lifting swing rod 134 connected to the pull rod 133, thereby keeping the end of the presser foot lifting crank 131 connected to the presser foot lifting roller 132 lifted and in contact with the first cam 121.

[0086] The outer contour of the first cam 121 includes a first area, which can be a continuous section on the outer contour of the first cam 121 and is used to cooperate with the presser foot lifting driving assembly 13. The first area is functionally divided into a presser foot lifting area and a press-down holding area 1213, wherein: when the presser foot lifting driving assembly 13 cooperates with the presser foot lifting area, the presser foot lifting driving assembly 13 completes the above action to switch the presser foot mechanism 200 to the presser foot lifting state; and when the presser foot lifting driving assembly 13 cooperates with the press-down holding area 1213, the presser foot lifting driving assembly 13 does not act, and the presser foot mechanism 200 maintains the press-down state.

[0087] In one embodiment, the first area includes a first presser foot lifting area 1211, a second presser foot lifting area 1212, and a press-down holding area 1213 connected therebetween. Specifically, in the initial state, the presser foot lifting roller 132 can stop in the press-down holding area 1213, and when the presser foot lifting roller 132 moves in the press-down holding area 1213, the presser foot lifting swing rod 134 does not move, and the presser foot mechanism 200 remains in the above-defined press-down state; the first cam 121 rotates clockwise or counterclockwise, so that the presser foot lifting roller 132 contacts any one of the first presser foot lifting area 1211 and the second presser foot lifting area 1212, and at this time, the presser foot lifting swing rod 134 can drive the presser foot mechanism 200 to perform the presser foot lifting action.

[0088] refer to Figure 1 and Figure 4 As shown in the figure, the second cam 122 drives the adjustment drive assembly 14 to move. Referring to the arrow direction indicated in the figure, when the drive member 12 rotates under the drive source 11, the second cam 122 rotates around Figure 4 The adjustment drive assembly 14 includes a first adjustment link 141, a second adjustment link 142, an adjustment crank 143, an adjustment roller 144 and a second elastic retainer 145 (marked at Figure 1 ). Among them:

[0089] The first adjusting link 141 has a second rotating center piece 1411 for connecting to the bracket 15, and the first adjusting link 141 can rotate around the central axis of the second rotating center piece 1411; one end of the first adjusting link 141 away from the second rotating center piece 1411 is connected to one end of the second adjusting link 142, and the adjusting roller 144 is rotatably connected to the middle of the first adjusting link 141. In the illustrated embodiment, the first adjusting link 141 is configured as a bent rod, and the adjusting roller 144 is rotatably connected to its bending point; the other end of the second adjusting link 142 is connected to one end of the adjusting crank 143; the other end of the adjusting crank 143 is connected to the eccentric shaft 31 in the adjusting mechanism 300, so as to drive the eccentric shaft 31 to rotate.

[0090] The second elastic retaining member 145 is mounted on the bracket 15 (both are marked on Figure 1) is used to keep the adjusting roller 144 in contact with the outer contour of the second cam 122, and the two form a follow-up matching relationship. A second area is provided on the second cam 122, and the second area can also be configured with a continuous contour in the contour of the second cam 122. The adjusting roller 144 is follow-up matched with the second area. When the driving member 12 rotates around the axis s1, the second cam 122 rotates and causes the adjusting roller 144 to roll in the second area, thereby driving the first adjusting link 141 to swing around the central axis of the second rotating center piece 1411 through the rolling contact between the two. Then, the second adjusting link 142 moves roughly in the direction indicated by the arrow in the figure, driving the adjusting crank 143 and the eccentric shaft 31 connected thereto to rotate in the direction indicated in the figure, thereby realizing the action of the adjusting mechanism 300. In this structure, the driving member 12 is also an active member, and the first adjusting link 141 is a driven member.

[0091] Combination Figure 1 , Figure 6 and Figure 7 As shown in FIG. 1 , there is only one driving source 11 in the linkage adjustment mechanism 100. Therefore, the driving member 12 rotates with the driving source 11 to realize three working states of the sewing machine: lifting the presser foot while feeding, lifting the presser foot while not feeding, and adjusting the gear position of the feed tooth frame 44 while the presser foot mechanism 200 is kept in the pressed state. Specifically, refer to FIG. Figure 7 As shown in the mark in, the second area on the second cam 122 includes the non-downfeeding area a, the gear adjustment area b, the transition area c, and the downfeeding area d. As mentioned above, in the initial state, the presser foot lifting roller 132 stops in the down-pressing holding area 1213, and correspondingly, the adjustment roller 144 is located in the gear adjustment area b.

[0092] (1) When the adjusting roller 144 rotates within the range of the gear adjustment area b, the adjusting drive assembly 14 can be slightly moved to rotate the feed tooth frame to any of the multiple gear positions. As shown above, in one embodiment, the feed tooth frame has angles corresponding to three working conditions: normal thickness fabric, thin material and thick material. Therefore, correspondingly, the feed tooth frame has three gears. When the adjusting roller 144 moves in the gear adjustment area b, the presser foot lifting roller 132 moves in the downward pressure holding area 1213, and the presser foot lifting drive assembly 13 does not move, so that the presser foot mechanism 200 remains in the downward pressure state. When the gear adjustment is completed, the head of the sewing machine can smoothly sew fabrics. In addition, gear adjustment is sometimes required during the sewing process. At this time, the gear switching of the feed tooth frame can also be performed in the above-mentioned manner.

[0093] (2) When there is a need to add material midway, the driving source 11 drives the driving member 12 to rotate a certain angle, and the regulating roller 144 moves in the non-downfeeding area a of the second cam 122 (refer to Figure 7, the second cam 122 rotates counterclockwise), and at the same time, the presser foot lifting roller 132 moves from the press holding area 1213 to the first presser foot lifting area 1211 of the first cam 121, realizing the presser foot lifting action. In this process, since the adjustment roller 144 enters the non-feeding area a after passing through the gear adjustment area b, at this time, the feed tooth frame is kept in the third gear (thick material working condition) position, and the presser foot plate is lifted, realizing the presser foot lifting and non-feeding at the same time. After the feeding is completed, the presser foot lifting action is reset, and the feed tooth frame is also reset to the original gear position.

[0094] It should be understood that no matter which gear position the feed tooth frame is in before, when adding materials midway, it will first be adjusted to the third gear (i.e., the thick material working condition), and then as the driving member 12 rotates further, the adjustment roller 144 enters the non-feeding zone a from the third gear position, and the feed tooth frame remains in the third gear position without further rotation. This method well solves the contradiction of lifting the presser foot but not feeding when adding materials midway. If the presser foot is lifted and the feed tooth frame is fed down at the same time when adding materials midway, when sewing starts again, when the feed tooth frame returns to a certain gear again, the feed teeth may cause the fabric to move slightly, and the sewing effect will be affected. In an embodiment with multiple gears, when adding materials midway, it is only necessary to adjust the feed tooth frame to any gear at which the feed teeth on the feed tooth frame can maintain contact with the fabric.

[0095] (3) When it is necessary to add fabric to the needle plate, the presser foot needs to be lifted and fed downward at the same time. At this time, the driving source 11 drives the driving member 12 to rotate clockwise (refer to Figure 7 In terms of the central position), the adjusting roller 144 moves through the transition area c and enters the lower supply area d, so that the adjusting mechanism 300 can adjust the feed tooth frame to the lower supply state; at the same time, the presser foot lifting roller 132 moves to the second presser foot lifting area 1212 of the first cam 121 to realize the presser foot lifting action.

[0096] It can be understood that although the feed tooth frame can have multiple gears, relatively speaking, the thickness of the fabric will not change very obviously. Therefore, the outline length of the gear adjustment area b (or the central angle corresponding to the gear adjustment area b) is not large, and the lower supply area d has a longer outline length (or the central angle corresponding to the lower supply area d is larger) in order to meet the travel requirements of the presser foot. By setting the transition area c connected between the gear adjustment area b and the lower supply area d, it can play a buffering and noise reduction effect, and prevent the feed tooth frame from generating noise or moving too fast during the state switching process. Specifically, the adjustment roller 144 on the first adjustment link 141 is in servo cooperation with the second cam 122, and if the transition area c is not set, the adjustment roller 144 will temporarily disengage from the servo cooperation with the second cam 122 at the position between the gear adjustment area b and the lower supply area d. When the two are in contact and cooperation again, the adjustment roller 144 collides with the second cam 122, generating noise and reducing the service life of the adjustment roller 144 and the second cam 122.

[0097] refer to Figure 8 and Fig. 9 As shown in Figure 8 and Fig. 9 Another embodiment of the linkage adjustment mechanism 100 is shown in FIG. 1 , which can achieve substantially the same functions. Figures 1 to 6 The linkage adjustment mechanism of the embodiment shown in FIG. 1 is different only in that the structure of the adjustment drive assembly 14 is slightly different. Fig. 9 As shown in the figure, the adjustment drive assembly 14 shown in the figure includes an adjustment crank 143, and an adjustment roller 144 connected to one end of the adjustment crank 143, and the other end of the adjustment crank 143 is connected to the concentric section 310 of the eccentric shaft 31 to drive the eccentric shaft 31 to rotate to complete the gear adjustment of the feed tooth frame.

[0098] Compared with the previous implementation, Figure 8 and Fig. 9 In the embodiment shown in , the first adjustment link 141 and the second adjustment link 142 in the adjustment drive assembly 14 are omitted, and the adjustment roller 144 is directly mounted on the adjustment crank 143. Adapting to the above structural changes of the adjustment drive assembly 14, the two ends of the second elastic retainer 145 are respectively connected to the bracket 15 and the adjustment crank 143 to keep the adjustment roller 144 reliably attached to the outer contour of the second cam 122.

[0099] It can be seen from the difference between the above two embodiments of the linkage adjustment mechanism 100 that there can be many variations of the presser foot lifting drive assembly 13 and the adjustment drive assembly 14, as long as the correct transmission of motion from the drive member 12 to the adjustment mechanism 300 and the presser foot mechanism 200 can be achieved. Correspondingly, the elastic retaining member used to keep the presser foot lifting roller 132 and the adjustment roller 144 in reliable contact with the corresponding outer contours of the drive member 12 can also be selected as a spring or a torsion spring as needed, and the appropriate installation position can be adaptively selected according to the needs of the design.

[0100] In addition, in the above two embodiments of the linkage adjustment mechanism 100, the follower that cooperates with the two cams in the driving member 12 is a roller. This structure can reduce the friction between the driving member 12 and the presser foot lifting crank 131 ( Figure 3 and Fig. 9 ), the first adjusting link 141 ( Figure 3 ), adjusting crank 143 ( Fig. 9 In other embodiments, the presser foot lifting roller and the adjusting roller structure can also be replaced by bearings to reduce contact friction. In addition, without considering wear, the presser foot lifting roller 132 and the adjusting roller 144 can also be omitted.

[0101] Reference Fig.10 and Fig.11 As shown in the figure, the structure of the driving member 12 of another embodiment is shown, which is different from the driving member 12 in the above two embodiments of the linkage adjustment mechanism 100, and the only difference is that: the first cam 121 and the second cam 122 are both provided with a slide groove 123, and the contour shape of the slide groove 123 is similar to Figure 7 The contour shapes shown in FIG. 1 are exactly the same, so the driving member 12 shown in the figure can be applied to the above-mentioned two linkage adjustment mechanisms 100 .

[0102] In adopting Fig.10 and Fig.11 When the driving component 12 is shown in the figure, the presser foot lifting roller 132 and the adjusting roller 144 correspond to form a sliding part that can cooperate with the groove section of the slide groove 123, but since this sliding part can rotate by itself, the friction between it and the slide groove 123 is rolling friction. It can be understood that in this embodiment with the slide groove 123, the presser foot lifting roller 132 and the adjusting roller 144 can also be set as a non-rotatable sliding part structure, and directly slide and rub with the slide groove 123. In addition, compared with the matching form of the outer contour of the matching cam, when the slide groove 123 is adopted, the presser foot lifting roller 132 and the adjusting roller 144 can always remain inseparable from the slide groove 123. Therefore, when the slide groove 123 is adopted, Fig.10 and Fig.11 When the driving member 12 is shown, the two elastic retaining members can be omitted.

[0103] It should be noted that in the aforementioned three embodiments of the linkage adjustment mechanism 100, the driving component 12 includes a two-part cam structure. In other embodiments, the driving component 12 may include two independent cams, and the two cams are installed on the two motion output ends of the output shaft of the same driving source 11. For example, in one embodiment, the driving source 11 is configured as a motor, and the output shaft of the motor extends to both sides. The two separately arranged cams can be respectively connected to the two end sides of the output shaft.

[0104] In addition, in the cam mechanism, the cam is used as the active member, and the slide groove on it or the outer contour shape of the cam itself determines the motion law of the follower that cooperates with it. The motion cooperation relationship in which the follower moves with the slide groove on the cam or the outer contour shape of the cam itself is called follow-up cooperation. For example, the cooperation relationship between the adjustment crank 143 equipped with the adjustment roller 144 and the outer wheel of the second cam 122, the cooperation relationship between the first adjustment connecting rod 141 equipped with the adjustment roller 144 and the outer wheel of the second cam 122, and the cooperation relationship between the presser foot lifting crank 131 equipped with the presser foot lifting roller 132 and the first cam 121, etc., are all called the follow-up cooperation between the corresponding rod and the corresponding cam. Similarly, when there is no roller between these rods and the first cam 121 and the second cam 122, but they are in direct contact cooperation, it is also called the follow-up cooperation between the corresponding rod and the corresponding cam. In addition, in the scheme where the slide groove 123 is provided on the cam, the corresponding rod may be retained in the slide groove 123 by other forms and move regularly with the shape of the slide groove 123. This matching relationship still belongs to follow-up matching.

[0105] refer to Fig.12 and Fig.13 As shown in the figure, another embodiment of the linkage adjustment mechanism 100 is shown, and the embodiment shown in the figure is different from Figure 8 and Fig. 9 The structure of the linkage adjustment mechanism 100 shown in FIG. 1 is substantially the same, except that the driving member 12 adopts a single cam structure. It can be expected by those skilled in the art that Fig.12 and Fig.13 The drive member 12 is also suitable for Figures 1 to 6 The linkage adjustment mechanism 100 in.

[0106] refer to Fig.13As shown in the figure, when the driving member 12 rotates clockwise, the adjusting roller 144 moves in contact with the gear adjustment area on the driving member 12, driving the adjusting crank 143 to adjust the gear of the feed tooth frame; when the driving member 12 rotates counterclockwise, the adjusting roller 144 moves in contact with the lower supply area on the driving member 12, driving the adjusting crank 143 to switch the feed tooth frame to the lower supply state, and at the same time, the presser foot lifting roller 132 moves in contact with the driving member 12 to realize the presser foot lifting action.

[0107] exist Fig.12 and Fig.13 In the illustrated embodiment, one end of the adjusting crank 143 cooperates with the second area on the second driving member 12, and the other end is provided with a connecting portion for connecting to the eccentric shaft 31. The connecting portion is provided with a selection connecting member 146, and the adjusting crank 143 can be connected / disconnected with the concentric segment 310 of the eccentric shaft 31 by selecting the connecting member 146. In the illustrated embodiment, the connecting portion is provided as an open annular member, and the selection connecting member 146 is inserted into the opening of the annular member. In addition, when the selection connecting member 146 releases the opening of the annular member, the sleeve connection between the annular member and the eccentric shaft 31 is also loosened, and the eccentric shaft 31 no longer rotates with the action of the adjusting crank 143.

[0108] When the working condition of adding materials in the middle is encountered, the optional connecting member 146 can be adjusted, for example, the connecting part set as an annular member is loosened from the socket state with the eccentric shaft 31, so that the connection relationship between the adjusting crank 143 and the eccentric shaft 31 is temporarily disconnected. At this time, the eccentric shaft 31 does not deflect with the swing of the adjusting crank 143, that is, the linkage adjustment mechanism 100 can only drive the presser foot to lift, but will not drive the feed tooth frame to rotate.

[0109] In addition, the optional connecting piece 146 can be temporarily loosened, and the relative angle between the adjusting crank 143 and the eccentric shaft 31 can be adjusted and then tightened again, so that the swing of the adjusting crank 143 after the angle is adjusted will not drive the eccentric shaft 31 to rotate. In this way, the presser foot can be lifted while the feed tooth frame does not rotate.

[0110] refer to Fig.14 and Fig.15 As shown in the figure, another embodiment of the linkage adjustment mechanism 100 is shown, and the embodiment shown in the figure is different from Figures 1 to 6 The structure of the linkage adjustment mechanism 100 shown in FIG. 1 is basically the same, except that the drive member 12 adopts a single cam structure with another profile. It can be understood that although in the illustrated embodiment, the adjustment drive assembly 14 adopts Figure 1 Figure 6 The structure shown in, however, Fig.14 and Fig.15 The driving member 12 in the embodiment is also applicable to Figure 8 and Fig. 9 In the linkage adjustment mechanism 100 shown in .

[0111] refer to Fig.15 As shown in FIG. , the drive member 12 is Fig.14 The driving source 11 in the embodiment drives the motor to rotate clockwise or counterclockwise, which can be Figures 1 to 6 Like the linkage adjustment mechanism 100 in the embodiment, the three working states of the sewing machine are realized: feeding while lifting the presser foot, feeding without lifting the presser foot, and the gear adjustment of the feed tooth frame 44. Specifically, refer to Fig.15 As shown in the mark, the cam structure as the driving member 12 mainly includes five outer contours (for ease of comparison with Figures 1 to 6 Corresponding to the implementation method in, the contours used to achieve the same functions are marked with the same marks): the second area for cooperating with the adjustment roller 144 includes the non-lower supply area a, the gear adjustment area b, and the lower supply area d; the first area for cooperating with the presser foot lifting roller 132 includes the first presser foot lifting area 1211 and the second presser foot lifting area 1212.

[0112] (1) In the initial state, the presser foot lifting roller 132 stops in the downward pressure holding area 1213, and correspondingly, the adjustment roller 144 is located in the gear adjustment area b.

[0113] (2) When the adjusting roller 144 rotates within the range of the gear adjustment area b, the adjusting drive assembly can be slightly moved to rotate the cloth feed tooth frame to any of the three gear positions. At the same time, the presser foot lifting roller 132 moves in the downward pressure holding area 1213, and the presser foot lifting drive assembly does not move, so that the presser foot mechanism 200 remains in the downward pressure state. When the gear adjustment is completed, the sewing machine head can smoothly perform sewing work. In addition, during the sewing process, gear adjustment is sometimes required. At this time, the gear of the cloth feed tooth frame can also be switched in the above manner.

[0114] (3) When there is a need to add material midway, the driving source 11 drives the driving member 12 to rotate a certain angle, and the regulating roller 144 moves in the non-downfeeding area a of the second cam 122 (refer to Fig.15 In the direction shown in FIG. 1 , the second cam 122 rotates clockwise), and at the same time, the presser foot lifting roller 132 moves from the press holding area 1213 to the first presser foot lifting area 1211 to achieve the presser foot lifting action. In this process, since the adjusting roller 144 enters the non-feeding area a after passing through the gear adjustment area b, at this time, the feed tooth frame is kept in the non-feeding state, and the presser foot plate is lifted, achieving the presser foot lifting and non-feeding at the same time.

[0115] (4) When it is necessary to add fabric to the needle plate, the presser foot needs to be lifted and fed downward at the same time. At this time, the driving source 11 drives the driving member 12 to rotate counterclockwise (refer to Fig.15In terms of the central position), the adjusting roller 144 moves to the lower supply area d, so that the adjusting mechanism 300 can adjust the cloth feeding tooth frame to the lower supply state; at the same time, the presser foot lifting roller 132 moves to the second presser foot lifting area 1212 to realize the presser foot lifting action.

[0116] refer to Fig.14 As shown in , along the axial direction of the driving member 12 rotating with the driving source 11, the first area and the second area are spaced or adjacent to each other. In the illustrated embodiment, the driving member 12 is configured as a body of equal cross-section, that is, along the axial direction of the driving member 12 rotating with the driving source 11, the cross-section of each part of the driving member 12 is the same. In this configuration, the first area and the second area can be staggered or adjacent to each other along the axial direction, that is, according to the illustrated manner, the presser foot lifting roller 132 is movably matched with the front outer contour of the driving member 12, and the adjusting roller 144 is movably matched with the rear outer contour of the driving member 12, so that the two areas of the driving member 12 can avoid each other, and the installation process of the linkage adjustment mechanism 100 is also convenient.

[0117] Understandable, although Fig.14 and Fig.15 The middle adjustment drive assembly adopts Figures 1 to 6 The connecting rod structure shown in Fig.14 and Fig.15 The driving member 12 in the embodiment is also applicable to Figure 8 and Fig. 9 The linkage adjustment mechanism 100 is shown.

[0118] The present invention also provides a sewing machine, which comprises the linkage adjustment mechanism 100 of any of the above embodiments. Moreover, due to the use of the linkage adjustment mechanism 100, the sewing machine can simultaneously have the working states of lifting the presser foot while feeding, lifting the presser foot while not feeding, and adjusting the gear position of the feed tooth frame.

[0119] It should be noted that: in the present invention, through the ingenious design of each contour area of ​​the driving member 12, one driving source 11 can drive the flexible switching of the three states of the sewing machine. Compared with the method of using independent driving sources to realize each function in the existing structure, the sewing machine in the present invention can obtain a more compact volume; at the same time, the driving source 11 in the present invention actually realizes three functions: the gear adjustment of the feed presser foot, the rotation and lowering of the feed tooth frame, and the presser foot lifting action of the presser foot mechanism. In comparison, in the existing technical scheme, one motor can only realize the presser foot lifting and lowering at the same time, but cannot realize the gear adjustment of the feed tooth frame and the presser foot lifting but not lowering. The scheme in the present invention solves the problem of keeping the feed tooth frame from lowering and keeping it in the third gear (i.e., thick material working condition) while lifting the presser foot. When adapting to the working condition of adding materials in the middle, the presser foot can be lifted to release the material while avoiding the movement of the fabric caused by the tooth frame being lifted again after lowering.

[0120] The technical features of the above-described embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the technical features in the above-described embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0121] The above-mentioned embodiments only express several implementation methods of the present invention, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the invention patent. It should be pointed out that, for ordinary technicians in this field, several variations and improvements can be made without departing from the concept of the present invention, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the patent of the present invention shall be subject to the attached claims.

Claims

1. A linkage adjustment mechanism for driving a presser foot mechanism (200) and a feed tooth frame (44) in a sewing machine, characterized in that: The cloth feeding tooth frame (44) comprises an active tooth frame (441) and a differential tooth frame (442), and the linkage adjustment mechanism (100) comprises a driving component (12), a presser foot lifting driving assembly (13) and an adjustment driving assembly (14), wherein: The driving member (12) is connected to a motion output end of the driving source (11) and is capable of rotating along with the driving source (11); The driving member (12) has a first area and a second area, the first area being used to form a follow-up cooperation with the presser foot lifting driving assembly (13) to drive the presser foot mechanism (200) to move; and, The second area is used to form a follow-up cooperation with the adjustment drive assembly (14) to drive the position of the feed tooth on the feed tooth frame (44) to change; The second area comprises a non-downfeeding area (a) and a downfeeding area (d); when the adjusting drive assembly (14) cooperates with the non-downfeeding area (a), the feed teeth on the feed tooth frame (44) are maintained in a non-downfeeding state; when the adjusting drive assembly (14) cooperates with the downfeeding area (d), the feed teeth on the feed tooth frame (44) are switched to a downfeeding state; The first area at least comprises two sections of presser foot lifting areas corresponding to the non-lower supply area (a) and the lower supply area (d), respectively; when the presser foot lifting driving assembly (13) cooperates with the presser foot lifting areas, the presser foot mechanism (200) can be switched to a presser foot lifting state by the presser foot lifting driving assembly (13) as the driving member (12) rotates.

2. The linkage adjustment mechanism according to claim 1, characterized in that: The second area comprises a gear adjustment zone (b), and the adjustment drive assembly (14) can cooperate with the gear adjustment zone (b) to drive the feed tooth frame (44) to rotate to perform gear switching.

3. The linkage adjustment mechanism according to claim 2, characterized in that: Along the direction in which the driving member (12) rotates with the driving source (11), the non-lower supply area (a) and the lower supply area (d) are respectively located on both sides of the gear adjustment area (b).

4. The linkage adjustment mechanism according to claim 3, characterized in that: The second region further includes a transition zone (c), and the transition zone (c) is connected between the gear adjustment zone (b) and the lower supply zone (d).

5. The linkage adjustment mechanism according to claim 2, characterized in that: The first area also includes a press-down holding area, which corresponds to the gear adjustment area (b). When the adjustment drive component (14) cooperates with the gear adjustment area (b), the presser foot lifting drive component (13) cooperates with the press-down holding area and keeps the presser foot pressed down.

6. The linkage adjustment mechanism according to claim 5, characterized in that: Along the direction in which the driving member (12) rotates with the driving source (11), the pressing and holding area is connected between the two sections of the presser foot lifting area.

7. The linkage adjustment mechanism according to any one of claims 1 to 6, characterized in that: The first area is configured as a continuously arranged cam profile, and / or the second area is configured as a continuously arranged cam profile.

8. A sewing machine, characterized in that: The sewing machine comprises the linkage adjustment mechanism described in any one of claims 1-7.

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