Embroidery machine and double-spindle driving device thereof

Abstract

The invention discloses an embroidery machine and a double-spindle driving device thereof, and belongs to the technical field of embroidery, the double-spindle driving device comprises a single driving motor and a driving clutch, and the single driving motor is matched with the driving clutch to drive one of a first driving shaft and a second driving shaft to rotate; and the driving clutch is used for realizing transmission separation and transmission connection between the single-driving motor and one of the first driving shaft and the second driving shaft and between the single-driving motor and the other driving shaft. Therefore, the first driving shaft and the second driving shaft can be driven by adopting a single motor, when one driving shaft rotates, the other driving shaft stops rotating, and independent and accurate driving of the first main shaft and the second main shaft can be realized by adopting single motor driving.

Description

Technical Field

[0001] This invention belongs to the technical field of embroidery equipment, specifically relating to embroidery machines. Background Technology

[0002] Referring to existing coil embroidery machines, a mounting beam extends laterally, and several coil embroidery heads are mounted on the mounting beam. To achieve flat embroidery, flat embroidery heads can be spaced apart between the coil embroidery heads. Each coil embroidery head (or other first-function head) is driven by a first main shaft, and each flat embroidery head (or other second-function head) is driven by a second main shaft. The first main shaft extends laterally and passes through the coil embroidery heads, and the second main shaft extends laterally and passes through the flat embroidery heads. In existing technology, a transmission assembly connects the first and second main shafts. Therefore, a drive motor is used to drive either the first or second main shaft, and the rotation of the first and second main shafts is achieved through the transmission assembly. However, this prevents the first and second main shafts from rotating independently, thus hindering independent and precise driving of both shafts. Summary of the Invention

[0003] In view of the shortcomings of the prior art, the technical problem to be solved by the present invention is to provide an embroidery machine and its dual spindle drive device, which can achieve independent and precise drive of the first spindle and the second spindle by using a single motor drive.

[0004] To solve the above-mentioned technical problems, the present invention adopts the following technical solution: First, a dual-spindle drive device for an embroidery machine is provided. The dual spindles include a first spindle and a second spindle. The first spindle is used to drive a first functional head, and the second spindle is used to drive a second functional head. The dual-spindle drive device includes: The first drive shaft is used to drive the first main shaft to rotate; The second drive shaft is used to drive the second main shaft to rotate, and the first drive shaft and the second drive shaft are spaced apart on the same axis. A single drive motor, in conjunction with a drive clutch, drives one of the first drive shafts and the second drive shaft to rotate. A drive clutch is used to achieve the transmission disengagement of a single drive motor from one of the first drive shaft and the second drive shaft, and the transmission connection of the other. The drive clutch includes an axial clutch component, a drive clutch motor, and a cam drive structure. During the clutching process, the drive clutch motor drives the axial clutch component to move axially through the cam drive structure, so as to achieve transmission separation from one of the first drive shaft and the second drive shaft and transmission connection with the other.

[0005] Preferably, the cam drive structure includes a drive cam connected to a drive clutch motor and a drive groove extending in the entire circumferential direction of the axial clutch member, wherein the cam portion of the drive cam engages with the drive groove.

[0006] Preferably, a roller is mounted on the cam portion, and the roller rolls in contact with the wall of the drive groove.

[0007] Preferably, the two ends of the axial clutch are respectively provided with strong magnets that attract each other to the ends of the first drive shaft and the second drive shaft.

[0008] Preferably, the ends of the first drive shaft and the second drive shaft are provided with clutch discs, and the two ends of the axial clutch are provided with a meshing transmission structure that cooperates with the clutch discs for transmission.

[0009] Preferably, the single drive motor is connected to a central drive shaft, and the axial clutch, the first drive shaft and the second drive shaft are bushing structures and are nested on the central drive shaft. A circumferential transmission structure is provided between the axial clutch and the central drive shaft, and the first drive shaft and the second drive shaft are circumferentially movable connected to the central drive shaft.

[0010] Preferably, the circumferential transmission structure is a key transmission structure between the central drive shaft and the axial clutch.

[0011] Preferably, a first belt drive assembly is provided between the first drive shaft and the first main shaft, and a second belt drive assembly is provided between the second drive shaft and the second main shaft.

[0012] Preferably, a transmission pulley is integrally provided on the first drive shaft and the second drive shaft.

[0013] Preferably, a transmission pulley is integrally provided on the first drive shaft and the second drive shaft.

[0014] In addition, an embroidery machine is provided, including the aforementioned dual spindle drive device.

[0015] The technical solution adopted in this invention has the following beneficial effects: A single drive motor drives both the first and second drive shafts, with only one shaft operating at a time. A drive clutch is provided to either disconnect or connect the single drive motor to the first and second drive shafts. Specifically, the single drive motor engages with the drive clutch to drive either the first or second drive shaft; when connected to the first drive shaft, it is disconnected from the second, and vice versa. Therefore, when the single drive motor drives either the first or second drive shaft, parameters such as speed and torque can be precisely adjusted. Independent and precise driving of both the first and second spindles can be achieved using a single motor. Furthermore, compared to using two separate drive motors to drive the first and second drive shafts, one motor is eliminated, reducing costs. Even with the addition of the drive clutch, the cost advantage remains significant.

[0016] Furthermore, the drive clutch includes an axial clutch component, a drive clutch motor, and a cam drive structure. During the clutch engagement process, the drive clutch motor drives the axial clutch component to move axially via the cam drive structure, thereby achieving transmission separation from one of the first and second drive shafts and transmission connection with the other. Its advantages lie in its compact structure and strong integration. The cam is directly coaxially arranged with the motor shaft, directly converting the motor's rotational motion into axial linear motion without the need for additional commutation, reduction, or linear transmission components (such as lead screws, gears, and racks). This effectively compresses the internal space of the motor, adapting to the design requirements of motor miniaturization and integration.

[0017] These features and advantages of the present invention will be disclosed in detail in the following specific embodiments and accompanying drawings. Attached Figure Description

[0018] The invention will be further described below with reference to the accompanying drawings: Figure 1 This is a schematic diagram of the dual spindle drive device in this invention; Figure 2 This is a schematic diagram of the dual spindle drive device in this invention (axial clutch is connected to the first drive shaft via transmission); Figure 3 This is a schematic diagram of the dual spindle drive device in this invention (axial clutch is connected to the second drive shaft for transmission); Figure 4 This is a schematic diagram of the dual spindle drive device in this invention (axial clutch is connected to the second drive shaft for transmission); Figure 5 This is a schematic diagram of the dual-spindle drive clutch structure in this invention (positioning element and second positioning disk). Figure 6This is a schematic diagram of the dual-spindle drive clutch structure in this invention (positioning element and first positioning disk). Figure 7 This is a schematic diagram of the dual spindle drive device in this invention; Figure 8 This is a schematic diagram of the dual spindle drive device in this invention; Figure 9 This is an exploded structural diagram of the transmission clutch component and clutch bearing in this invention; Figure 10 This is a schematic diagram of the transmission structure between the two transmission clutches and the first and second main shafts in this invention; Figure 11 This is a schematic diagram of the transmission structure between the two transmission clutches and the first and second main shafts in this invention; Figure 12 This is a partial structural schematic diagram of the multi-head embroidery machine in this invention; Reference numerals: Dual spindle drive device 100, first drive shaft 110, clutch disc 111, toothed groove 1111, drive pulley 112, flange 113, second drive shaft 120, single drive motor 130, central drive shaft 131, drive clutch 140, axial clutch component 141, drive groove 1411, convex tooth 1412, spline 1413, strong magnet 1414, drive clutch motor 142, drive cam 143, roller 1431, positioning disc 150, positioning groove 151, positioning assembly 160, positioning rod 161, positioning drive motor 162, first connecting rod 163, second connecting rod 164, position sensor 170, first proximity switch 171, second proximity switch 172, rear mounting bracket 180, bearing housing 181, connecting plate 182; Dual-spindle transmission device 200, first spindle 210, first transmission section 211, second transmission section 212, second spindle 220, transmission clutch assembly 230, first transmission clutch 231, second transmission clutch 232, transmission clutch component 233, clutch bearing 2331, bearing outer ring 23311, bearing inner ring 23312, radial protrusion 23313, clamping part 23314, clutch sleeve 2332, clutch clamp 2333, transmission clutch motor 234, motor bracket 2341, lead screw nut assembly 235, clutch slider 236, first slider 2361, second slider 2362, U-shaped connecting part 2363, clutch bracket 237, clutch mounting plate 2371, transverse side plate 2372, through groove 2373, clutch guide rail 238, transmission belt assembly 240; Mounting beam 300, embroidery head 310, flat embroidery head 320. Detailed Implementation

[0019] The technical solutions of the embodiments of the present invention will be explained and described below with reference to the accompanying drawings. However, the following embodiments are only preferred embodiments of the present invention and not all of them. Other embodiments obtained by those skilled in the art based on the embodiments in the implementation methods without creative effort are all within the protection scope of the present invention.

[0020] Those skilled in the art will understand that, without conflict, the features in the following embodiments and implementations can be combined with each other.

[0021] The terminology used in this invention is for the purpose of describing particular embodiments only and is not intended to limit the invention. For example, terms such as "upper," "lower," "front," "rear," and "lateral," which indicate orientation or positional relationship, are based solely on the orientation or positional relationship shown in the accompanying drawings and are used only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device / element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention.

[0022] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "fixation," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0023] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0024] Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features.

[0025] Referring to existing multi-head embroidery machines that combine flat embroidery and ribbon embroidery, there is a mounting beam extending laterally and several ribbon embroidery heads and several flat embroidery heads mounted side by side on the front side of the mounting beam. The ribbon embroidery heads and flat embroidery heads are spaced apart along the lateral extension direction of the mounting beam, so that ribbon embroidery and flat embroidery can work separately as needed.

[0026] In this embodiment, the extension direction of the mounting beam is defined as transverse, and the direction perpendicular to the mounting beam is defined as front-to-back. The ribbon embroidery head is driven by a first main shaft, and the flat embroidery head is driven by a second main shaft. The first and second main shafts are spaced apart vertically, with the first main shaft above and the second main shaft below. The first main shaft extends laterally and passes through several ribbon embroidery heads, and the second main shaft extends laterally and passes through several flat embroidery heads. Additionally, shuttle boxes are located below the ribbon and flat embroidery heads, and a lower shaft extends laterally and passes through several shuttle boxes. The first and second main shafts are connected by a first transmission assembly, and the second main shaft is connected to the lower shaft by a second transmission assembly. The first and second transmission assemblies are typically belt assemblies.

[0027] In this way, when the flat embroidery head is working, the lower shaft is driven to rotate by the second main shaft. When the ribbon embroidery head is working, the first main shaft can drive the second main shaft to rotate, which in turn drives the lower shaft to rotate. Thus, whether the flat embroidery head or the ribbon embroidery head is working, the first and second main shafts, as well as the lower shaft, can all rotate through the transmission of the first and second transmission components, allowing the shuttle box to cooperate with the head for embroidery. However, this also causes some parts of the flat embroidery head to idle while the ribbon embroidery head is working, resulting in unnecessary wear and affecting the service life.

[0028] Reference Figures 1 to 12 As shown, the multi-head embroidery machine of this embodiment can avoid the situation where some parts of the flat embroidery head are idle when the ribbon embroidery head is working, without changing the transmission relationship between the first main shaft, the second main shaft and the lower shaft.

[0029] This embodiment takes the combination of a ribbon embroidery head 310 and a flat embroidery head 320 as an example. The ribbon embroidery head 310 and the flat embroidery head 320 are combined and installed on the mounting beam 300, and a dual spindle drive device 200 is correspondingly provided to realize the transmission of the first spindle 210 and the second spindle 220. The dual spindle drive device 200 includes: The first main shaft 210 has a first transmission section and a second transmission section arranged in the same direction. The second main shaft 220 has a first transmission section and a second transmission section arranged in the same direction. Furthermore, the first transmission section of the first main shaft 210 is connected to the disc embroidery machine head, and the first transmission section of the second main shaft 220 is connected to the flat embroidery machine head. A transmission belt assembly 240 is provided between the second transmission sections of the first main shaft 210 and the second transmission sections of the second main shaft 220. Specifically, a synchronous transmission belt can be used, and synchronous pulleys connected to the synchronous transmission belt are installed on the two main shafts.

[0030] In addition, it also includes a transmission clutch assembly 230, which is provided with two transmission clutches, namely a first transmission clutch 231 and a second transmission clutch 232, which are respectively connected to the first main shaft 210 and the second main shaft 220. That is, they are respectively used to realize the separation or transmission connection of the first transmission segment 211 and the second transmission segment 212 on the first main shaft 210 and the second main shaft 220, and only one of the first transmission segment and the second transmission segment of the first main shaft 210 and the second main shaft 220 are connected at the same time.

[0031] The coaxial arrangement of the first and second transmission sections here means that the first and second transmission sections are separated along the same axis with a certain gap between them. This allows both the first and second transmission sections to rotate independently without affecting each other when the transmission clutch is not engaged. Furthermore, the diameters of the first and second transmission sections can be equal. Additionally, the second transmission section is shorter than the first transmission section, sufficient for connection to the transmission belt assembly 240 and the second transmission assembly.

[0032] In this way, when the flat embroidery machine head is working, the first and second transmission sections of the second main shaft are connected, while the first and second transmission sections of the first main shaft are separated. Therefore, although the second main shaft can drive the second transmission section of the first main shaft to rotate, the first transmission section of the first main shaft does not rotate, and the corresponding components of the ribbon embroidery machine head will not idle. Similarly, when the ribbon embroidery machine head is working, the first and second transmission sections of the first main shaft are connected, while the first and second transmission sections of the second main shaft are separated. Therefore, although the first main shaft can drive the second transmission section of the second main shaft to rotate, the first transmission section of the second main shaft does not rotate, and the corresponding components of the flat embroidery machine head will not idle, thus preventing the components of the flat embroidery machine head and the ribbon embroidery machine head from idling when not in operation.

[0033] Taking the first transmission clutch as an example, the transmission clutch includes a transmission clutch component 233 and a clutch drive component. The clutch drive component drives the transmission clutch component 233 to move axially, so as to realize the separation or transmission connection between the transmission clutch component 233 and the first transmission section 211 and the second transmission section 212.

[0034] In some embodiments, the clutch drive includes a drive clutch motor 234 and a lead screw and nut assembly 235. The drive clutch motor 234 drives the lead screw and nut assembly 235, and the nut of the lead screw and nut assembly 235 is connected to the drive clutch component 233. The lead accuracy of the lead screw and nut assembly (especially the ball screw) can reach the micrometer level, and the displacement is strictly linearly related to the motor rotation angle. This allows for precise control of the axial travel of the drive clutch component, ensuring consistent engagement lengths and effective disengagement between the drive clutch component and the first and second transmission sections, thus improving the reliability of the clutch action. Alternatively, a ball screw can be used in conjunction with the motor's brake function to achieve reliable position locking.

[0035] Furthermore, the transmission clutch also includes a clutch slider 236 connected to the nut and the transmission clutch component 233. Therefore, the nut drives the clutch slider 236 to move linearly, and the clutch slider 236 drives the transmission clutch component 233 to move linearly. The transmission clutch also includes a clutch bracket 237, on which the first main shaft 210 and the second main shaft 220 are rotatably supported. A clutch guide rail 238 is mounted on the clutch bracket 237, and the clutch slider 236 is connected to the clutch guide rail 238. The sliding fit between the clutch guide rail and the clutch slider strictly limits the stroke accuracy of the clutch slider, ensuring that the engagement / disengagement of the transmission clutch is completed along a predetermined trajectory. The clutch bracket 237 brings together the core components of the clutch operation, such as the clutch guide rail 238, the clutch slider 236, the transmission clutch motor 234, and the lead screw and nut assembly 235, forming a unified whole from previously separate components.

[0036] Specifically, the clutch slider 236 includes a first slider 2361 connected to the clutch guide rail 238 and a second slider 2362 connected to the clutch drive component (i.e., the nut of the lead screw nut assembly 235). The second slider 2362 is provided with a U-shaped connecting part 2363, which is connected to the transmission clutch component 233. Furthermore, the first slider 2361 and the second slider 2362 can be separately installed and connected by a connector. The first and second sliders are rigidly linked, and the driving force is transmitted from the second slider to the first slider without loss, achieving a clutch action of "unconstrained driving and interference-free guidance," ensuring both efficient transmission of driving force and high precision of the sliding trajectory.

[0037] Here, the first transmission clutch 231 and the second transmission clutch 232 share a clutch bracket 237. The clutch bracket 237 includes a clutch mounting plate 2371 and transverse side plates 2372 connected to the transverse sides of the clutch mounting plate. One end of the transverse side plate 2372 is connected to the clutch mounting plate 2371, and the other end is connected to the mounting beam 300. The transmission clutch motor 234 is mounted on the clutch mounting plate 2371 via an L-shaped motor bracket 2341, and the clutch guide rail 238 is also mounted on the clutch mounting plate 2371. In addition, the clutch mounting plate 2371 is provided with a through groove 2373. The second slider 2362 passes through the through groove 2373, thereby being located on the first side of the clutch mounting plate 2371 and connected to the nut, and on the second side and connected to the transmission clutch component 233.

[0038] It is understandable that the method of changing the direction of motion of the clutch drive is not limited to the aforementioned lead screw and nut structure; for example, a gear and rack structure can be used as a replacement.

[0039] In some embodiments, the transmission clutch 233 is a bushing structure, and a keyed transmission structure is provided between the transmission clutch 233 and the first transmission segment 211 and the second transmission segment 212. For example, the outer circumference of the first and second transmission segments is provided with spline grooves, that is, the first and second transmission segments are splined shaft structures, and the transmission clutch 233 is provided with splines that mate with the spline grooves. The transmission clutch 233 is always connected to the first transmission segment 211, but its connection to or separation from the second transmission segment 212 is achieved through axial sliding. When connected to the second transmission segment 212, the first and second transmission segments 211 and 212 achieve synchronous rotation through the connection of the transmission clutch 233.

[0040] Specifically, the transmission clutch 233 is located between the two transverse side plates 2372. Based on the working principle of the transmission clutch 233, it can slide axially and rotate, but the connection between the clutch slider 236 and the transmission clutch 233 must not affect the rotation of the transmission clutch 233. To meet the above requirements, the transmission clutch 233 includes a clutch bearing 2331, a clutch sleeve 2332, and a clutch clamp 2333. The clutch bearing 2331 has an outer bearing ring 23311 and an inner bearing ring 23312. The clutch sleeve 2332 is fixed to the inner bearing ring 23312 by the clutch clamp 2333. The inner ring of the clutch sleeve 2332 has a spline that mates with the spline grooves on the outer circles of the first transmission section 211 and the second transmission section 212. The bearing inner ring 23312 includes a raceway portion at the axial center and two clamping portions 23314 on both sides. Balls are provided between the raceway portion and the bearing outer ring 23311. The clamping portions 23314 are wider than the bearing outer ring 23311 in the axial direction, allowing the clutch clamp 2333 to clamp onto the outside of the clamping portion 23314, thus fixing the bearing inner ring 23312 to the clutch sleeve 2332. Additionally, the bearing outer ring 23311 has two radially distributed protrusions 23313 circumferentially. The radially distributed protrusions 23313 have fixing holes for connecting fixing bolts, thereby connecting to the two ends of the U-shaped connecting portion 2363 of the second slider. In this way, the transmission clutch 233 can move axially as a whole through the key transmission structure. Simultaneously, due to the clutch bearing 2331, the clutch sleeve 2332 and the outer ring of the clutch bearing can rotate relative to each other, but the clutch slider 236 and the outer ring 23311 do not rotate. Therefore, the first transmission section 211 and the second transmission section 212 achieve synchronous rotation through the connection of the clutch sleeve 2332, without interfering with the clutch slider 236. Because of the use of two separate clutch clamps, the tightening torque of each clamp can be adjusted separately during installation to accurately calibrate the coaxiality between the clutch sleeve and the inner ring of the bearing. The two clutch clamps respectively clamp onto both ends of the inner ring of the bearing, simultaneously restricting the axial relative displacement and circumferential relative rotation between the clutch sleeve and the inner ring of the bearing. Compared to a single clamp structure that can only limit movement on one side, the double clamps prevent the clutch sleeve from experiencing unilateral movement or circumferential slippage during torque transmission or axial sliding, ensuring that the clutch sleeve and the inner ring of the bearing always maintain a coaxial rigid connection. When the double clamps are arranged symmetrically, the clamping force is evenly distributed on both ends of the axial direction of the inner ring of the bearing. This can effectively avoid local stress concentration caused by a single clamp, prevent plastic deformation of the inner ring of the bearing from occurring, or elliptical deformation of the clutch sleeve due to pressure on one side. This avoids the risk of increased spline fit clearance and decreased meshing accuracy.

[0041] Furthermore, the clutch sleeve 2332 is composed of two equal-length sleeve shaft sections spliced ​​together in the axial direction. Deep-hole spline machining of long sleeves is prone to axial straightness deviations and spline tooth profile distortion, especially when the clutch sleeve is long, making it difficult to guarantee full-length accuracy in terms of the machining equipment's stroke and tool rigidity. After splitting into two equal-length shaft sections, the single-piece machining length is halved, the tool force during spline machining is more stable, and tooth profile accuracy and coaxiality are easier to control. Simultaneously, the two shaft sections can be standardized for mass production, offering strong interchangeability and reducing production quality control costs. Moreover, the two shaft sections are correspondingly fixed to the engagement parts at both ends of the bearing inner ring. During assembly, they can be fixed to the engagement parts on both sides of the bearing inner ring using clutch clamps at both ends, achieving symmetrical constraint between the clamps and the shaft sections. Compared to an integral sleeve, this structure avoids the problem of "one end fixed tightly, one end loose" caused by excessive axial length of the sleeve, ensuring the coaxiality of the clutch sleeve and the bearing inner ring and reducing radial runout during spline engagement. In actual operation, there may be slight coaxiality errors between the first transmission section 211 and the second transmission section 212 (such as cumulative installation errors or axial misalignment caused by operational vibration). The symmetrical weight distribution of the two equal-length shaft sections, combined with the symmetrical clamping force of the double clamps, ensures that the axial stress of the clutch sleeve is evenly transmitted to the engagement part of the bearing inner ring. This avoids local stress concentration caused by uneven axial weight in the integral sleeve, prevents bending deformation of the sleeve, and ensures smooth axial sliding. A small adaptive clearance can be maintained at the connection of the two spliced ​​sleeve sections. When there is a deviation between the axes of the two transmission sections, the two shaft sections can precisely engage with the splines of the corresponding transmission sections, and the coaxial deviation can be offset by fine-tuning the clearance. This avoids spline jamming and accelerated wear caused by rigid constraints in the integral sleeve.

[0042] It is understood that the transmission clutch 233 is not limited to the clutch bearing structure mentioned above. For example, the outer circle of the transmission clutch is provided with an annular groove, and the clutch slider is provided with a clutch fork. The clutch fork is located in the annular groove to drive the transmission clutch 233 to move axially.

[0043] In order to drive the first spindle 210 and the second spindle 220, the multi-head embroidery machine in this embodiment is also provided with a dual spindle drive device 100.

[0044] In this embodiment, the dual spindle drive device 100 includes: The first drive shaft 110 is used to drive the first main shaft 210 to rotate; The second drive shaft 120 is used to drive the second main shaft 220 to rotate; A first transmission belt assembly is provided between the first drive shaft 110 and the first main shaft 210, and a second transmission belt assembly is provided between the second drive shaft 120 and the second main shaft 220. Specifically, a first transmission belt assembly is provided between the first drive shaft 110 and the first transmission section 211 of the first main shaft, and a second transmission belt assembly is provided between the second drive shaft 120 and the first transmission section 211 of the second main shaft. The first drive shaft 110 and the second drive shaft 120 are located on the rear side of the mounting beam, and the mounting beam has through holes for the first and second transmission belt assemblies to pass through. The first and second transmission belt assemblies can specifically use synchronous transmission belts, and synchronous pulleys connected to the synchronous transmission belts are installed on the two shafts that are connected to the transmission belts. Belt drives have strong compatibility with the center distance between the drive shaft and the main shaft, thus allowing the dual main shaft drive device 100 to be arranged on the rear side of the mounting beam.

[0045] In some embodiments, a first drive motor and a second drive motor are provided, wherein the first drive motor is used to drive the first drive shaft to rotate; and the second drive motor is used to drive the second drive shaft to rotate.

[0046] The output shaft of the first drive motor and the first drive shaft can be directly driven by a coupling, and the output shaft of the second drive motor and the second drive shaft can also be directly driven by a coupling. Alternatively, a belt drive assembly can be used. Thus, the transmission structure between the first drive motor and the second transmission section of the first main shaft forms a complete transmission chain, which can be disengaged by the first transmission clutch 231. The transmission structure between the second drive motor and the second transmission section of the second main shaft forms another complete transmission chain, which can be disengaged by the second transmission clutch 232.

[0047] During ribbon embroidery, the first drive motor drives the first drive shaft to rotate, and the first drive shaft drives the first main shaft to rotate via the first transmission belt assembly. During flat embroidery, the second drive motor drives the second drive shaft to rotate, and the second drive shaft drives the second main shaft to rotate via the second transmission belt assembly. This allows for precise control of the first and second drive motors separately according to the different needs of ribbon embroidery and flat embroidery. It is understood that the first and second drive motors can be geared motors with reducers, or a separate reducer can be installed, which is then connected to the first and second drive shafts.

[0048] However, the first and second drive motors have higher power and cost, and only one of them can operate at a time. Therefore, in some embodiments, a single drive motor 130 can be used to drive the first drive shaft 110 and the second drive shaft 120, and only one of the first drive shaft 110 and the second drive shaft 120 can operate at a time. Therefore, a drive clutch 140 is provided to achieve transmission separation or connection between the single drive motor 130 and the first drive shaft 110 and the second drive shaft 120. That is, the single drive motor 130 cooperates with the drive clutch 140 to drive one of the first drive shaft 110 and the second drive shaft 120; when the single drive motor 130 is connected to the first drive shaft 110, it is disconnected from the second drive shaft 120; similarly, when the single drive motor 130 is connected to the second drive shaft 120, it is disconnected from the first drive shaft 110. Thus, the single drive motor 130 can form a complete transmission chain through the transmission structure between the drive clutch 140 and the second transmission section of the first main shaft, and another complete transmission chain through the transmission structure between the drive clutch 140 and the second transmission section of the second main shaft. The drive source for both transmission chains shares the single drive motor 130. The first transmission chain can be disconnected by the first transmission clutch 231, and the second transmission chain can be disconnected by the second transmission clutch 232. Therefore, the arrangement of the drive clutch 140 and the two transmission clutches allows for flexible switching and adjustment of the transmission chains.

[0049] Using a single drive motor to drive the first and second drive shafts reduces the number of drive motors compared to using two separate drive motors, thus lowering costs. Even with the addition of a drive clutch, the cost advantage remains significant.

[0050] Moreover, although only a single drive motor is set, the inherent advantages of dual drive motors can still be retained. When the single drive motor drives the first drive shaft or the second drive shaft, parameters such as speed and torque can be precisely adjusted accordingly. Independent and precise driving of the first and second spindles can be achieved by using a single motor drive.

[0051] In some embodiments, the first drive shaft 110 and the second drive shaft 120 are spaced apart on the same axial direction, and the drive clutch 140 includes an axial clutch member 141, which moves axially during the clutching process to achieve transmission separation or transmission connection with the first drive shaft 110 and the second drive shaft 120.

[0052] Specifically, the single drive motor 130 is connected to a central drive shaft 131, and the two can be coaxially arranged, connected by a coupling to the output shaft of the single drive motor 130 and the central drive shaft 131. The axial clutch 141, the first drive shaft 110, and the second drive shaft 120 are all bushing structures, nested on the central drive shaft. The axial clutch 141 is slidably nested on the central drive shaft 131. The axial positions of the first drive shaft 110 and the second drive shaft 120 on the central drive shaft are relatively fixed, and they are axially separated with a large gap between them. The axial clutch 141 is disposed within this gap, providing a certain axial movement space. Therefore, when the axial clutch 141 is connected to one of the first drive shaft 110 or the second drive shaft 120, the other can be disengaged from the axial clutch 141, allowing both the first drive shaft 110 and the second drive shaft 120 to rotate independently without affecting each other. Furthermore, the structures of the first drive shaft 110 and the second drive shaft 120 can be identical. The axial clutch, the first drive shaft, and the second drive shaft are all bushing structures nested on the central drive shaft. All components are arranged coaxially, which greatly compresses the radial space of the transmission system and avoids the volume redundancy problem caused by the parallel arrangement of multiple shafts.

[0053] In some embodiments, a keyed drive structure is provided between the central drive shaft 131 and the axial clutch 141. For example, a spline groove is provided on the central drive shaft 131, i.e., a splined shaft structure is provided, and a spline 1413 is provided on the inner ring of the axial clutch. The cooperation between the key and the keyway can strictly limit the relative rotation between the axial clutch and the central drive shaft, ensuring that the torque of the central drive shaft can be transmitted to the axial clutch in a 1:1 ratio, with no slippage, no torque loss, and high transmission efficiency. Moreover, the keyed drive does not restrict the axial movement of the axial clutch, perfectly matching the functional requirement that the clutch needs to slide along the central axis to switch between the clutch states with the first and second drive shafts.

[0054] In this embodiment, the two ends of the axial clutch 141 are respectively provided with a convex-concave engagement transmission structure that mates with the ends of the first drive shaft and the second drive shaft. Specifically, two protruding teeth 1412 are evenly distributed circumferentially at both ends of the axial clutch 141, while two tooth grooves 1111 are correspondingly provided at the ends of the first drive shaft 110 and the second drive shaft 120. The protruding teeth 1412 mesh with the tooth grooves 1111. Alternatively, three or four protruding teeth 1412 can be provided to engage with the tooth grooves 1111. Therefore, the axial clutch 141 can slide axially along the central drive shaft 131, and the central drive shaft 131 can also drive the axial clutch 141 to rotate, thereby allowing the axial clutch 141 to drive the first drive shaft 110 or the second drive shaft 120 to rotate.

[0055] To establish a convex-concave interlocking transmission structure, a clutch disc 111 and a drive pulley 112 are sequentially provided axially at the ends of the first drive shaft 110 and the second drive shaft 120. The diameter of the clutch disc 111 is larger than the diameter of the drive pulley 112. The clutch disc 111 has toothed grooves 1111 on its end face. The drive pulley 112, as part of the first and second transmission belt assemblies, is the transmission pulley for connecting the transmission belts. Correspondingly, the first and second main shafts have driven pulleys connected to the transmission. The clutch disc 111 and the drive pulley 112 can be integrally formed and connected to the first drive shaft 110 and the second drive shaft 120, or they can be integrally formed with the first drive shaft 110 and the second drive shaft 120. The advantage of integral formation is that no additional assembly procedures are required, and coaxiality is easily guaranteed.

[0056] Understandably, the single drive motor 130 is equipped with an encoder that can detect the angular displacement and angular velocity of the motor shaft, thereby providing precise position and speed feedback signals for the closed-loop control of the motor. Furthermore, based on the encoder feedback, the single drive motor 130 is controlled so that the axial clutch 141 rotates to a set angle each time, ensuring that the convex tooth 1412 corresponds circumferentially with the tooth groove 1111. That is, the drive shaft 131 of the single drive motor 130 remains at the set angle to ensure the convex tooth and tooth groove correspond, thus achieving engagement.

[0057] In addition, the drive clutch 140 also includes a drive clutch motor 142 that drives the axial clutch member 141 to move axially. To convert the rotation of the drive clutch motor 142 into the axial movement of the axial clutch member 141, the drive clutch 140 further includes a drive cam 143, the cam portion of which is eccentrically positioned. The axial clutch member 141 has a drive groove 1411 extending throughout the entire circumferential direction, and the cam portion of the drive cam 143 engages with the drive groove 1411. The output shaft of the drive clutch motor 142 is connected to the drive cam 143. During the rotation of the drive cam 143, it can drive the axial clutch member 141 to move axially. The cam portion of the drive cam is always located in the drive groove 1411 and does not interfere with the rotation of the axial clutch member 141. It is understood that the axial length of the drive groove can be perfectly matched with the stroke design of the drive cam profile. The maximum axial movement distance of the axial clutch member is directly limited by the end point of the groove, without the need for additional limit switches or stops. This mechanical limiting method is far more reliable than electronic limiting, effectively preventing over-engagement or incomplete disengagement of the clutch due to uncontrolled overtravel, thus protecting the clutch mechanism and motor spindle. Furthermore, the use of a drive cam 143 in conjunction with a drive groove 1411 offers the following advantages: 1. Precise and controllable motion: The cam's profile curve can be precisely customized through design, strictly limiting the stroke, speed, and acceleration trajectory of the axial clutch component. For example, during clutch engagement, a motion curve of low-speed engagement → uniform movement → low-speed locking can be designed to avoid impact collisions between the clutch component and the meshing tooth surface; during disengagement, rapid disengagement can be achieved, reducing wear time in the semi-engaged state. 2. Compact structure and strong integration: The cam is directly coaxially arranged with the motor shaft, directly converting the motor's rotational motion into axial linear motion without the need for additional commutation, reduction, or linear transmission components (such as lead screws, gears, and racks). This effectively compresses the internal space of the motor, adapting to the design requirements of motor miniaturization and integration. 3. High force transmission efficiency and fast response speed: The cam and axial clutch have line or point contact, resulting in a short transmission chain and low energy loss. It can quickly convert motor torque into axial thrust of the clutch. For applications requiring high-frequency clutch switching, millisecond-level clutch response can be achieved. 4. Good action repeatability and stable clutch precision: After the cam profile is machined, its motion trajectory has unchanging consistency. The displacement deviation of the axial clutch during each clutch operation is minimal, preventing "partial clutch" states caused by transmission backlash or pressure fluctuations. This ensures precise clutch engagement / disengagement and improves the reliability of the motor drive.

[0058] In some embodiments, a roller 1431 may also be installed on the cam portion. The roller may be a rolling bearing, with its axis perpendicular to the axis of the axial clutch 141. Without the roller, the cam portion and the drive groove of the axial clutch are in surface contact sliding friction. During the clutch process, the resistance generated by the relative movement of the two is large, and it is easy to cause wear and deformation of the contact surface, resulting in a decrease in clutch stroke accuracy. After adding the roller, the contact form becomes line contact rolling friction between the roller and the drive groove. The coefficient of friction can be reduced to 1 / 10 to 1 / 20 of sliding friction, which not only reduces the energy consumption of the motor driving the cam, but also avoids abrasive wear on the contact surface, significantly extending the service life of the cam and the drive groove. The roller is a wear part and can be specially customized from wear-resistant bearing steel or engineering ceramics. The installation method is a modular and detachable structure. When the roller wears out, only the roller needs to be replaced to restore performance, without replacing the more expensive cam or axial clutch, greatly reducing maintenance difficulty and cost.

[0059] Furthermore, the axial clutch 141 is provided with strong magnets 1414 at both ends, which are attracted to the ends of the first drive shaft 110 and the second drive shaft 120, respectively. These magnets are attracted to the end faces of the clutch disc 111, whose diameter is substantially the same as the diameters of both ends of the axial clutch 141. Thus, when the axial clutch 141 is connected to the first drive shaft 110 or the second drive shaft 120, the magnetic attraction of the strong magnets allows the axial clutch to be precisely and coaxially engaged with the drive shaft. The strong magnets 1414 firmly hold the two together, and they can only be separated when the clutch motor 142 drives the clutch to engage. Moreover, the attraction force of the strong magnets directly serves as the locking preload force between the clutch and the drive shaft, eliminating the need for additional mechanical locking structures, spring clamping devices, or electromagnetic locking mechanisms, significantly simplifying the connection structure between the axial clutch and the drive shaft. Combining the axial displacement design driven by a cam, the entire clutch system consists of only a "fitting transmission structure + magnetic positioning + cam-driven separation," resulting in fewer parts and lower assembly difficulty, meeting the design requirements for miniaturized and integrated clutch motors. During clutch engagement, the clutch motor only needs to overcome the attraction force of the strong magnet to separate the clutch component from the drive shaft, without needing to overcome the rigid resistance of the mechanical locking structure or the clamping force of the spring. Compared to traditional mechanical clutches, magnetic clutches require less drive torque, allowing for the use of a lower-power clutch motor, thus reducing overall system energy consumption and cost.

[0060] Specifically, both ends of the axial clutch 141 are provided with end plates, which serve as the side walls of the drive groove 1411. At the same time, the end plates are provided with two radial convex surfaces that intersect perpendicularly to form a cross-shaped convex surface. The first radial convex surface has magnet mounting grooves on both radial sides for mounting strong magnets 1414, and the other radial convex surface has protruding teeth 1412 on both radial sides.

[0061] Since the axial clutch 141 is connected to the first drive shaft 110 and the second drive shaft 120 by the meshing of the convex teeth and grooves at a circumferentially set angle, according to the above description, the single drive motor 130 can drive the central drive shaft 131 to stay at the set angle each time. However, after the axial clutch is disengaged from one of the first drive shaft and the second drive shaft, if the first drive shaft and the second drive shaft continue to rotate, it is still difficult to guarantee that the convex teeth and grooves between the axial clutch and the first drive shaft and the second drive shaft will re-mesh when the clutch is engaged next time.

[0062] Therefore, in some embodiments, in order to ensure that the circumferential positions of the teeth and grooves between the axial clutch member and the first and second drive shafts correspond each time the clutch is engaged or disengaged, a drive shaft positioning structure can be provided to circumferentially position the first drive shaft 110 and the first drive shaft 120 to restrict their rotation. Specifically, the positioning is performed on the first drive shaft 110 and the second drive shaft 120 after they are disengaged from the axial clutch member 141, that is, only one of the first drive shaft 110 and the second drive shaft 120 is positioned at the same time. When the axial clutch member 141 is disengaged from the first drive shaft 110, the first drive shaft 110 is positioned, and when it is disengaged from the second drive shaft 120, the second drive shaft 120 is positioned.

[0063] In some embodiments, the drive shaft positioning structure includes two positioning disks 150 corresponding to the first drive shaft 110 and the second drive shaft 120, namely the first positioning disk and the second positioning disk, and a positioning component 160. When the positioning component 160 is in a positioning state with one of the first and second positioning disks, it is disengaged from the other. That is, after the axial clutch 141 is disengaged from the first drive shaft 110, the positioning component 160 is in a positioning state with the first positioning disk and in a disengaged state with the second positioning disk; after the axial clutch 141 is disengaged from the second drive shaft 120, the positioning component 160 is in a positioning state with the second positioning disk and in a disengaged state with the first positioning disk. Therefore, the drive shaft positioning structure and the disengagement process between the axial clutch 141 and the first drive shaft 110 and the second drive shaft 120 form a cooperation.

[0064] Furthermore, the outer rings of the first and second positioning disks are provided with positioning grooves 151. When the positioning component 160 is inserted into the positioning groove 151, it is in a positioning state with the corresponding positioning disk, and the positioning disk and the corresponding drive shaft cannot rotate. Since the positioning component forms a rigid engagement with the side wall of the positioning groove after insertion, it directly limits the circumferential rotational freedom of the positioning disk, and the engagement is gapless, achieving zero axial movement and circumferential locking, thus achieving precise circumferential positioning of the first and second drive shafts.

[0065] In some embodiments, the positioning assembly 160 includes a positioning rod 161 and a positioning driver. The positioning driver is connected to both ends of the positioning rod 161. When one end of the positioning rod is raised and disengaged from the corresponding positioning slot 151, the other end descends and inserts into the corresponding positioning slot 151. The up-and-down swinging motion of the positioning rod is completed on the outside of the positioning plate. The movement trajectory has no spatial overlap with the axial linear movement of the axial clutch and the directional sliding of the clutch slider along the guide rail. Furthermore, the positioning rod only swings and inserts after the axial clutch is completely separated from the drive shaft, completely avoiding collisions and interference with the clutch components and ensuring the independence and coordination of the actions of each component.

[0066] Specifically, the positioning driver includes two positioning drive motors 162, which drive the two ends of the positioning rod 161 to rise and fall accordingly. Further, the positioning driver includes two linkage assemblies connecting the positioning drive motors 162 and the positioning rod 161. Each linkage assembly includes a first linkage 163 and a second linkage 164. The first end of the first linkage 163 is fixed to the output shaft of the positioning drive motor 162, and the second end of the first linkage 163 is hinged to one end of the second linkage 164. The second end of the second linkage 164 is hinged to the end of the positioning rod 161. The first linkage 163 is shorter, acting like a cam, thus driving the second linkage 164 to move up and down, thereby causing the end of the positioning rod 161 to rise and fall. When one of the first linkages 163 is at the bottom, the other first linkage 163 is at the top. Two positioning drive motors drive the two ends of the positioning rod, breaking free from the fixed constraints of a single-drive "mechanical linkage for one lift and one drop." Through independent forward / reverse rotation, speed adjustment, and stroke control of the motors, precise control of the positioning rod's swing angle, insertion depth at both ends, and lifting speed is achieved. The linkage assembly, acting as the transmission intermediary between the motors and the positioning rod, is crucial for the precise mechanical conversion between the motor's rotational motion and the positioning rod's linear lifting / swinging around a fulcrum. Simultaneously, it utilizes the lever transmission characteristics of the linkage to amplify the driving force, resolving the problems of "mismatched motion, insufficient driving force, and hard contact impact" inherent in direct motor drive. The combination of dual motors and dual linkages, along with the design of the linkage assembly, allows the positioning drive motors and linkage assembly to be offset from the front of the positioning plate to its side, avoiding the movement space of the clutch, slider, and guide rail. This solves the layout challenges of a coaxial dual-drive shaft clutch system with limited space and dense components. Moreover, the dual motors and dual connecting rods are symmetrically arranged on both sides of the positioning rod fulcrum, so that the forces at both ends are synchronous and balanced when driving the positioning rod. Compared with the off-center load problem of single driver driving on one side, the force distribution of the positioning rod is thoroughly optimized, which greatly improves the rigidity and stability of the positioning lock.

[0067] It can be understood that both positioning drive motors 162 are equipped with encoders, which can detect the angular displacement and angular velocity of the motor shaft, thereby providing accurate position and speed feedback signals for the closed-loop control of the motor. Moreover, based on the feedback from the encoders, the two positioning drive motors 162 are controlled so that the first link 163 rotates to a set angle each time, thereby ensuring that when one of the first links 163 is below, the other first link 163 is above. Ultimately, this ensures that when one end of the positioning rod rises and disengages from the corresponding positioning slot 151, the other end descends and inserts into the corresponding positioning slot 151.

[0068] Understandably, two positioning elements can be set to replace one positioning rod. Two positioning drive motors or linear actuators such as electromagnets can drive the two positioning elements to extend and retract axially in the first drive shaft 110 and the second drive shaft 120, thereby allowing the positioning elements to be inserted into or disengaged from the positioning groove.

[0069] In this embodiment, two positioning grooves 151 are provided on the outer rings of the first and second positioning disks at 180-degree intervals along the circumference. This provides two circumferential alignment engagement points for the positioning rod, completely solving the problem of "requiring precise calibration of the circumferential angle between the positioning rod and the groove, and preventing insertion even with a slight deviation" in single positioning grooves, and significantly reducing the circumferential alignment requirements during processing, assembly, and clutch switching. Additionally, a position sensor 170 is provided on the outer side of the outer rings of the first and second positioning disks to detect whether the positioning component is engaged with the positioning groove. Specifically, the position sensor 170 has two proximity switches to detect whether the first connecting rod 163 is approaching. The two proximity switches are a first proximity switch 171 and a second proximity switch 172, with the first proximity switch 171 below and the second proximity switch 172 above. Thus, when the first connecting rod 163 rotates to the lower position, the first proximity switch 171 can sense it, at which point the positioning groove of one corresponding positioning disk engages with the positioning rod; when the first connecting rod 163 rotates to the upper position, the second proximity switch 172 can sense it, at which point the positioning groove of one corresponding positioning disk separates from the positioning rod. The switching signal output by the position sensor serves as a hard interlock for triggering / disabling the axial clutch, positioning drive motor, and clutch slider drive, completely solving the problems of timing errors and action conflicts in purely mechanical linkages or non-interlocked electronic controls, and achieving seamless and orderly linkage of the "clutch-positioning" action.

[0070] Furthermore, the first drive shaft 110 and the second drive shaft 120 are also provided with flange portions 113, which are fixed to the positioning plate 150. Bolts are evenly connected along the circumference of the flange portion 113 to fix the flange portion 113 to the positioning plate 150. The flange portion 113, the clutch plate 111, and the drive pulley 112 can be integrally set or separately fixed to form the first drive shaft 110 and the second drive shaft 120.

[0071] As a variation, the drive clutch motor can also drive a clutch fork through a lead screw and nut assembly. The clutch fork is located in the drive slot and drives the axial clutch component to move axially.

[0072] Additionally, a rear mounting bracket 180 is installed on the rear side of the mounting beam. The rear mounting bracket 180 includes two bearing housings 181 and a connecting plate 182 connecting the two bearing housings. A motor bracket is installed on the side of one of the bearing housings for mounting a single drive motor 130, while a drive clutch motor 142 is installed on the connecting plate 182. The two bearing housings are used to support the central drive shaft 131.

[0073] The ribbon embroidery head and the flat embroidery head are two different embroidery heads with different functions, which can be referred to as the first function head and the second function head. It is understood that the combination of the ribbon embroidery head and the flat embroidery head can also be replaced by other two types of function heads. In addition, this embodiment describes part of the structure of the embroidery machine, and other structures can be referred to the prior art.

[0074] The above description is merely a specific embodiment of the invention, but the scope of protection of the invention is not limited thereto. Those skilled in the art should understand that the invention includes, but is not limited to, the contents described in the accompanying drawings and the specific embodiments above. Any modifications that do not depart from the functional and structural principles of the invention will be included within the scope of the claims.

Claims

1. A dual-spindle drive device for an embroidery machine, comprising a first spindle and a second spindle, wherein the first spindle drives a first functional head and the second spindle drives a second functional head, characterized in that... The dual spindle drive device includes: The first drive shaft is used to drive the first main shaft to rotate; The second drive shaft is used to drive the second main shaft to rotate, and the first drive shaft and the second drive shaft are spaced apart on the same axis. A single drive motor, in conjunction with a drive clutch, drives one of the first drive shafts and the second drive shaft to rotate. A drive clutch is used to achieve the transmission disengagement of a single drive motor from one of the first drive shaft and the second drive shaft, and the transmission connection of the other. The drive clutch includes an axial clutch component, a drive clutch motor, and a cam drive structure. During the clutching process, the drive clutch motor drives the axial clutch component to move axially through the cam drive structure, so as to achieve transmission separation from one of the first drive shaft and the second drive shaft and transmission connection with the other.

2. The dual-spindle drive device for an embroidery machine according to claim 1, characterized in that, The cam drive structure includes a drive cam connected to a drive clutch motor and a drive groove extending in the entire circumferential direction of the axial clutch component, wherein the cam portion of the drive cam engages with the drive groove.

3. The dual-spindle drive device for an embroidery machine according to claim 2, characterized in that, A roller is mounted on the cam section, and the roller rolls in contact with the wall of the drive groove.

4. The dual-spindle drive device for an embroidery machine according to claim 3, characterized in that, The two ends of the axial clutch are respectively provided with strong magnets that attract each other to the ends of the first drive shaft and the second drive shaft.

5. The dual-spindle drive device for an embroidery machine according to claim 1, characterized in that, The ends of the first drive shaft and the second drive shaft are provided with clutch discs, and the two ends of the axial clutch are provided with a meshing transmission structure that cooperates with the clutch discs for transmission.

6. The dual-spindle drive device for an embroidery machine according to claim 1, characterized in that, The single drive motor is connected to a central drive shaft. The axial clutch, the first drive shaft, and the second drive shaft are bushing structures and are nested on the central drive shaft. A circumferential transmission structure is provided between the axial clutch and the central drive shaft. The first drive shaft and the second drive shaft are circumferentially movable connected to the central drive shaft.

7. The dual-spindle drive device for an embroidery machine according to claim 6, characterized in that, The circumferential transmission structure is a key transmission structure between the central drive shaft and the axial clutch.

8. The dual-spindle drive device for an embroidery machine according to claim 1, characterized in that, A first belt drive assembly is provided between the first drive shaft and the first main shaft, and a second belt drive assembly is provided between the second drive shaft and the second main shaft.

9. The dual-spindle drive device for an embroidery machine according to claim 8, characterized in that, A transmission pulley is integrally provided on the first drive shaft and the second drive shaft.

10. An embroidery machine, characterized in that, The invention includes a dual spindle drive device for an embroidery machine as described in any one of claims 1 to 9.

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