Revolution-based self-rotation driving method, structure and extruder used therein

Abstract

The revolution-based self-rotation drive method, structure and the extruder used therein include a power output shaft with a revolution motion trajectory, a self-rotation drive device and a transition transmission device. The power output shaft is extended and arranged along the Z axis. From the transmission relationship, the transition transmission device is located between the power output shaft and the self-rotation drive device. It is characterized in that the power output shaft and the transition transmission device are connected in transmission and maintain relative motion coordination in the direction of the first axis, and the transition transmission device and the self-rotation drive device are connected in transmission and maintain relative motion coordination in the direction of the second axis. The first axis and the second axis are respectively perpendicular to the Z axis, and when viewed along the Z axis, the angle between the first axis and the second axis is not equal to zero. The beneficial technical effect is that the self-rotation output torque of any size can be selected and configured within a continuous and stepless range by adjusting the matching dimensions between the transition transmission device and the self-rotation drive device and the power output shaft.

Description

Technical Field

[0001] The present invention relates to a mechanical drive method, and more particularly to a rotational drive method based on revolution, which can output both revolution torque and rotation torque. The present invention also relates to a structure for implementing the drive method, and an extruder using the drive method and structure. Background Art

[0002] In the field of mechanical processing, it is often necessary to use an actuator that can simultaneously complete rotation and revolution. For example, the patent CN201510407898.9 discloses a coaxial output rotation and revolution device, which includes a power input shaft, a power output shaft, a transition gear system and a KHV small tooth difference planetary gear system. The power of the power input shaft is transmitted to the KHV small tooth difference planetary gear system through the transition gear system. The power input shaft includes a main shaft and a crank shaft. The axis of the power output shaft coincides with the axis of the crank shaft of the power input shaft. The power output shaft revolves around the main shaft axis of the power input shaft at a speed equal to the speed of the power input shaft. The main power of the power input shaft is superimposed by the transition gear system and the KHV small tooth difference planetary gear system, so that the power output shaft generates a rotation motion at the same speed and in the opposite direction as the power input shaft. At the same time, the thrust bearing coaxial with the power output shaft for rotation and revolution and the thrust bearing coaxial with the main shaft of the power input shaft are used in series to bear the axial load. The KHV small-tooth-difference planetary gear system includes internal and external gears and output planetary gears. The power take-off shaft is mounted in the spoke holes of the output planetary gears. Rotation of the internal and external gears drives the power take-off shaft through the output planetary gears. The power take-off shaft's rotational output torque is directly proportional to the module m of the output planetary gears and the internal and external gears. The module m is also directly proportional to the eccentricity L between the output planetary gears and the internal and external gears. Therefore, selecting a larger module m to increase the power take-off shaft's rotational output torque also increases the eccentricity L between the output planetary gears and the internal and external gears, requiring more installation space. Furthermore, it's important to note that the module m is a standardized parameter, which means that the power take-off shaft's rotational output torque options are quantized, rather than being stepless. Summary of the Invention

[0003] The aforementioned problem of the PTO shaft's autorotational output torque being quantized in steps is due to the inherent characteristics of the gear pair's meshing transmission. This cannot be solved by simply changing the gear structure; instead, a radical change must be made to the transmission structure between the autorotational drive source and the PTO shaft. In light of this, the present invention proposes a novel autorotational drive method and structure that not only drives the PTO shaft in autorotation without hindering its orbital revolution, but also enables the PTO shaft's autorotational output torque to be configured within a continuous, stepless range.

[0004] In view of this, the present invention first proposes a self-rotation driving method based on revolution, comprising a power output shaft with an orbital motion trajectory, a self-rotation driving device and a transition transmission device, wherein the power output shaft extends and is arranged along the Z axis direction, and from the transmission relationship point of view, the transition transmission device is interposed between the power output shaft and the self-rotation driving device; it is characterized in that the power output shaft and the transition transmission device are connected in transmission and maintain relative motion coordination in the first axis direction, and the transition transmission device and the self-rotation driving device are connected in transmission and maintain relative motion coordination in the second axis direction, the first axis and the second axis are respectively perpendicular to the Z axis, and when viewed along the Z axis direction, the angle between the first axis and the second axis is not equal to zero; by utilizing the above-mentioned coordination motion between the transition transmission device and the self-rotation driving device and the power output shaft, while not hindering the revolution of the power output shaft, the self-rotation driving device can drive the power output shaft to self-rotate through the transition transmission device when it rotates.

[0005] Secondly, the present invention also proposes a rotation drive structure based on revolution, comprising a power output shaft having a revolution motion trajectory, a rotation drive device and a transition transmission device, wherein the power output shaft extends and is arranged along the Z axis direction, and from the transmission relationship point of view, the transition transmission device is between the power output shaft and the rotation drive device; it is characterized in that the transition transmission device is transmission-connected to the power output shaft and maintains relative motion cooperation in the first axis direction, and can drive the power output shaft to rotate when the transition transmission device rotates; at the same time, the rotation drive device and the transition transmission device are transmission-connected and maintain relative motion cooperation in the second axis direction, and can drive the transition transmission device to rotate when the rotation drive device rotates; the first axis and the second axis are respectively perpendicular to the Z axis, and when viewed along the Z axis direction, the angle between the first axis and the second axis is not equal to zero; the transition transmission device is used for the above-mentioned cooperation with the rotation drive device and the power output shaft, and cooperates with the rotation drive device to drive the power output shaft to rotate without hindering the revolution of the power output shaft.

[0006] A further technical solution may also be that the transition transmission device is respectively provided with a first sliding joint arranged along the first axis direction and a second sliding joint arranged along the second axis direction, the power output shaft and the first sliding joint maintain relative motion cooperation in the first axis direction, and the self-rotation drive device and the second sliding joint maintain relative motion cooperation in the second axis direction.

[0007] A further technical solution may be that the power output shaft includes a coupling shaft section, the coupling shaft section is used to form a transmission connection with the transition transmission device, and the rotation center line of the coupling shaft section is consistent with the rotation center line of the power output shaft; the coupling shaft section includes a first retaining device, and the first retaining device is used to define a reference for movement along the first axis direction; the first sliding coupling portion of the transition transmission device maintains relative movement and is engaged with the first retaining device.

[0008] A further technical solution may be that the transition transmission device further includes a first cavity, and the first retaining device is retained in the first cavity.

[0009] A further technical solution may be that the first cavity has a first side cavity wall arranged along the first axial direction, the first side cavity wall constitutes the first sliding joint, and the inner side edge of the first side cavity wall rests on the first retaining device and maintains relative movement cooperation with the first retaining device.

[0010] A further technical solution may be that, in the direction of the first axis, the width of the first cavity reserved for the first retaining device to move is greater than the width of the first retaining device itself so as not to hinder the revolution of the power output shaft.

[0011] A further technical solution may also be that the first sliding joint of the transition transmission device is in the shape of a rod, the first retaining device of the coupling shaft segment is a cavity-shaped tunnel, the tunnel passes through the center of the coupling shaft segment along the first axis direction, the center line of the tunnel is located on the center line of the cross section of the coupling shaft segment, the first sliding joint is inserted into the tunnel and maintains a sliding fit in the direction of the first axis.

[0012] A further technical solution may be that the self-rotation drive device includes a second retaining device arranged along the second axis direction, and the second retaining device is used to define a reference for movement along the second axis direction; the second sliding joint on the transition transmission device maintains relative movement and is engaged with the second retaining device.

[0013] A further technical solution may be that the self-rotation drive device further includes a second cavity, and the second sliding joint is retained in the second cavity.

[0014] A further technical solution may be that the second mold cavity has a second side cavity wall arranged along the second axial direction, the second side cavity wall constitutes the second retaining device, and the second sliding joint rests on the inner side edge of the second side cavity wall and maintains relative movement cooperation with the second side cavity wall.

[0015] A further technical solution may be that, in the direction of the second axis, the width of the second cavity reserved for the second sliding joint to move is much larger than the width of the second sliding joint itself so as not to hinder the revolution of the power output shaft.

[0016] A further technical solution may be that the autorotation drive device includes a autorotation drive gear, the second cavity is arranged on the spoke of the autorotation drive gear, the rotation center line of the second cavity is consistent with the rotation center line of the autorotation drive gear, and the autorotation drive gear and the transition transmission device are transmission connected and maintain relative motion cooperation in the direction of the second axis.

[0017] A further technical solution may further include a housing, wherein the self-rotating drive device and the power output shaft are disposed within the housing, with one end of the power output shaft extending out of the housing. In this way, the housing serves as an outer protective layer for the self-rotating drive device and the power output shaft, preventing damage caused by direct collisions with foreign objects and shielding them from debris such as dust and metal particles, thereby maintaining the cleanliness and transmission accuracy of the self-rotating drive device and the power output shaft and effectively extending their service life.

[0018] The power take-off shaft is inevitably subjected to axial loads in specific applications. If the power take-off shaft undergoes axial displacement under the action of the axial load, it is very likely to destroy the power transmission relationship between the power take-off shaft and the transition transmission device. In view of this, a further technical solution can also be provided, wherein a step is further provided on the power take-off shaft, and one end face of the transition transmission device rests on the step; and a stopper is also included, which is positioned on the self-rotating drive gear by a screw and presses against the other end face of the transition transmission device. In this way, the transition transmission device is confined between the stopper and the step of the power take-off shaft, and the axial load borne by the power take-off shaft can be transmitted to the self-rotating drive gear through the step, the transition transmission device, and the stopper in sequence, thereby improving the power take-off shaft's ability to resist axial loads.

[0019] A further technical solution can also be that left and right revolving drive gears are also arranged in the housing, the self-rotation drive device includes a self-rotation drive gear, the self-rotation drive gear is located between the left and right revolving drive gears, the revolving drive gear and the self-rotation drive gear are respectively rotatably arranged on the housing through bearings; the power output shaft is rotatably offset on the spokes of the revolving drive gear so as not only to allow the power output shaft to rotate on the revolving drive gear, but also the revolving drive gear can drive the power output shaft to revolve around the rotation center line of the revolving drive gear, and the rotation center line of the revolving drive gear is consistent with the rotation center line of the self-rotation drive gear. According to the above technical solution, the revolving axis of the power output shaft is consistent with the rotation center line of the revolving drive gear and the rotation center line of the self-rotation drive gear.

[0020] A further technical solution may also include a power input shaft, a gear set, and a power distribution shaft. The power input shaft is connected to the power distribution shaft through a reduction gear set, and the power distribution shaft is then connected to the revolution drive gear and the rotation drive gear through the gear set. The gear set allows the power output shaft to rotate in the opposite direction to the revolution direction but at the same speed.

[0021] In addition, the present invention also proposes an extruder that uses the above-mentioned revolution-based self-rotation drive structure, which is characterized in that it includes the above-mentioned revolution-based self-rotation drive structure and an eccentric rotor volume pulsation deformation plasticizing extrusion device, and the power output shaft is connected to the rotor of the eccentric rotor volume pulsation deformation plasticizing extrusion device.

[0022] According to the above-mentioned revolution-based self-rotation drive method and revolution-based self-rotation drive structure, compared with the prior art, the beneficial technical effect of the present invention is that: since the transition transmission device is used for the above-mentioned cooperation with the self-rotation drive device and the power output shaft, without hindering the revolution of the power output shaft, it cooperates with the self-rotation drive device to drive the power output shaft to form self-rotation. In this way, by adjusting the cooperation dimensions between the transition transmission device and the self-rotation drive device and the power output shaft, any size of self-rotation output torque can be selected and configured within a continuous and stepless range, getting rid of the dilemma of the existing patent CN201510407898.9 that the self-rotation output torque of the power output shaft is in direct proportion to the standardized parameter of the output planetary gear and the internal and external gears - the module m, and it also has the characteristics of simple structure and easy disassembly and replacement.

[0023] Since the present invention has the above characteristics and advantages, it can be applied to a self-rotation driving method and structure based on revolution and an extruder used therein. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 It is a schematic cross-sectional view of an extruder with a revolution-driven self-rotation structure to which the technical solution of the present invention is applied;

[0025] Figure 2 1 is a schematic diagram of the three-dimensional structure of the revolution-based rotation drive structure 100, in which the housing 1 is omitted;

[0026] Figure 3 is a schematic cross-sectional structural diagram of the transition transmission device 4;

[0027] Figure 4 is a schematic cross-sectional structural diagram of the coupling shaft section 21 of the power output shaft 2;

[0028] Figure 5 3 is a schematic side structural diagram of the self-rotating drive gear 3;

[0029] Figure 6 It is along Figure 1 Schematic diagram of the dynamic changes of the revolution-based rotation drive structure 100 viewed from the AA direction;

[0030] Figure 7 is a schematic cross-sectional structural diagram of a revolution-based rotation drive structure 100a according to the third embodiment;

[0031] Figure 8 is a schematic cross-sectional structural diagram of a revolution-based rotation drive structure 100b according to a fourth embodiment;

[0032] Figure 9 is a schematic cross-sectional structural diagram of a revolution-based rotation drive structure 100c according to a basic implementation method;

[0033] Figure 10 Schematic diagram of the revolution trajectory of the power output shaft 2c. DETAILED DESCRIPTION

[0034] The following further describes the revolution-based self-rotation driving method, structure and extruder applied to the technical solution of the present invention in conjunction with the accompanying drawings.

[0035] First, basic implementation methods

[0036] like Figure 9 and Figure 10 As shown, a rotation drive method based on revolution includes a power output shaft 2c with a revolution motion trajectory, a rotation drive device 3c and a transition transmission device 4c, wherein the power output shaft 2c is along the Z axis ( Figure 9 、 Figure 10, and the transition transmission device 4c is arranged to extend in the direction of the Z axis (not shown). From the perspective of transmission relationship, the transition transmission device 4c is interposed between the power output shaft 2c and the self-rotation drive device 3c; it is characterized in that the power output shaft 2c and the transition transmission device 4c are connected in transmission and maintain relative movement cooperation in the direction of the first axis T7, and the transition transmission device 4c and the self-rotation drive device 3c are connected in transmission and maintain relative movement cooperation in the direction of the second axis T8, the first axis T7 and the second axis T8 are respectively perpendicular to the Z axis, and when viewed along the Z axis, the angle between the first axis T7 and the second axis T8 is not equal to zero, and of course is not equal to 180 degrees or 360 degrees; by utilizing the above-mentioned cooperation movement between the transition transmission device 4c and the self-rotation drive device 3c and the power output shaft 2c, while not hindering the revolution of the power output shaft 2c, the self-rotation drive device 3c can drive the power output shaft 2c to form self-rotation through the transition transmission device 4c when it rotates.

[0037] In addition, the present invention also proposes a rotation drive structure 100c based on revolution. Figure 9 and Figure 10 As shown, the self-rotation drive structure 100c shown includes a power output shaft 2c with a revolution motion trajectory, a self-rotation drive device 3c and a transition transmission device 4c, the power output shaft 2c is extended and arranged along the Z axis direction, and from the transmission relationship point of view, the transition transmission device 4c is between the power output shaft 2c and the self-rotation drive device 3c; it is characterized in that the transition transmission device 4c is connected to the power output shaft 2c in a transmission manner and maintains relative motion coordination in the direction of the first axis T7, and when the transition transmission device 4c rotates, it can drive the power output shaft 2c to rotate; at the same time, the self-rotation drive device 3c and the transition transmission The transition transmission device 4c is connected to the self-rotation drive device 3c and maintains relative motion cooperation in the direction of the second axis T8. When the self-rotation drive device 3c rotates, it can drive the transition transmission device 4c to rotate; the first axis T7 and the second axis T8 are respectively perpendicular to the Z axis, and when viewed along the Z axis, the angle between the first axis T7 and the second axis T8 is not equal to zero; the transition transmission device 4c is used for the above-mentioned cooperation with the self-rotation drive device 3c and the power output shaft 2c, and cooperates with the self-rotation drive device 3c to drive the power output shaft 2c to form self-rotation without hindering the revolution of the power output shaft 2c.

[0038] The power output shaft 2c has two motion forms, namely, rotation around its central axis O1 and revolution around its revolution axis O. The central axis O1 and the revolution axis O do not overlap.

[0039] Among them, from the perspective of transmission relationship, the transition transmission device 4c is located between the power output shaft 2c and the self-rotation drive device 3c. The above characteristics define that the transition transmission device 4c is a power transmission component between the power output shaft 2c and the self-rotation drive device 3c, which is used to transmit the self-rotation torque of the self-rotation drive device 3c to the power output shaft 2c, driving the power output shaft 2c to rotate.

[0040] The three-dimensional coordinate system established by the first axis T7, the second axis T8, and the Z-axis is a movable coordinate system that moves with the position of the power output shaft 2c. Furthermore, the first axis T7 and the second axis T8 rotate about the Z-axis in a plane perpendicular to the Z-axis as the power output shaft 2c rotates. As viewed along the Z-axis, an angle θ is maintained between the first axis T7 and the second axis T8. The angle θ can be 30°, 60°, or 90°, but not 0°, 180°, or 360°. In this embodiment, the angle θ is 90°.

[0041] The transition transmission device 4c and the power output shaft 2c maintain relative motion in the direction of the first axis T7. The above characteristics define that the self-rotating drive structure 100c is provided with a first movable space for allowing the power output shaft 2c to move in the direction of the first axis T7. The power output shaft 2c moves relative to the transition transmission device 4c in the direction of the first axis T7 to form a first motion trajectory d1. Secondly, the self-rotating drive device 3c and the transition transmission device 4c maintain relative motion in the direction of the second axis T8. The above characteristics define that the self-rotating drive structure 100c is also provided with a second movable space for allowing the transition transmission device 4c to move in the direction of the second axis T8. Since the power output shaft 2c moves relative to the transition transmission device 4c, the power output shaft 2c can actually also move within the second movable space. The power output shaft 2c moves relative to the self-rotating drive device 3c in the direction of the second axis T8 to form a second motion trajectory d2. According to the above analysis, it can be inferred that the motion trajectory of the power output shaft 2c on the plane defined by the first axis T7 and the second axis T8 is a circular synthetic orbital trajectory with the orbital axis O as the center and R as the radius. , which is conducive to the revolution of the power output shaft 2c.

[0042] In order to achieve power transmission between the transition transmission device 4c and the power output shaft 2c and the self-rotating drive device 3c, the transition transmission device 4c is further provided with a first sliding joint 41c arranged along the first axis T7 and a second sliding joint 42c arranged along the second axis T8. The power output shaft 2c and the first sliding joint 41c maintain relative motion in the direction of the first axis T7, and the self-rotating drive device 3c and the second sliding joint 42c maintain relative motion in the direction of the second axis T8. The first sliding joint 41c can be a structure integrally formed with the transition transmission device 4c, or it can be a component that is separate from the transition transmission device 4c and mounted on the transition transmission device 4c. The first sliding joint 41c is configured with a guide mechanical structure arranged along the first axis T7, but this does not rule out the possibility that the first sliding joint 41c can also be arranged in other directions. For example, the first sliding joint 41c may be a flat surface arranged not only along the first axis T7 but also along the Z axis. It may also be a three-dimensional structure, such as a guide groove. It may also be a pulley assembly arranged along the first axis T7. In this embodiment, the first sliding joint 41c is a first dovetail groove arranged along the first axis T7. The second sliding joint 42c has the same definition as the first sliding joint 41c and is not further described here. In this embodiment, the second sliding joint 42c is a second dovetail groove arranged along the second axis T8.

[0043] To achieve power transmission between the power output shaft 2c and the transition transmission device 4c, the power output shaft 2c further includes a coupling shaft segment 21c, which is used to form a transmission connection with the transition transmission device 4c. The rotation centerline of the coupling shaft segment 21c is consistent with the rotation centerline O1 of the power output shaft 2c. The coupling shaft segment 21c includes a first retaining device 211c, which is used to define a reference for movement along the first axis T7. The first sliding coupling portion 41c of the transition transmission device 4c is engaged with the first retaining device 211c to maintain relative movement. The first retaining device 211c can be a structure integrally formed with the coupling shaft segment 21c, or a component separately provided from the coupling shaft segment 21c and mounted on the coupling shaft segment 21c. The first retaining device 211c can be a plane arranged along the first axis T7, a guide groove, or a pulley set arranged along the first axis T7. In this embodiment, the first sliding joint 41c is a first dovetail groove arranged along the first axis T7, and the first retaining device 211c is a first dovetail slider arranged along the first axis T7. The first dovetail slider slides within the first dovetail groove. This allows the power output shaft 2c to slide relative to the intermediate transmission device 4c in the direction of the first axis T7 and, when the intermediate transmission device 4c rotates, to rotate under the influence of the intermediate transmission device 4c. The first sliding joint 41c and the first retaining device 211c form a kinematic pair that maintains relative motion between the coupling shaft segment 21c and the intermediate transmission device 4c in the direction of the first axis T7. Furthermore, the first retaining device 211c defines a reference for movement along the first axis T7. This feature defines the first sliding joint 41c's movement along the first axis T7 with the first retaining device 211c as the reference. However, since the intermediate transmission device 4c and the coupling shaft segment 21c are in relative motion, the first sliding joint 41c and the first retaining device 211c can also be considered to define each other as a reference.

[0044] To achieve power transmission between the self-rotation drive device 3c and the transition transmission device 4c, the self-rotation drive device 3c further includes a second retaining device 321c arranged along the second axis T8. The second retaining device 321c is used to define a reference for movement along the second axis T8. The second sliding joint 42c on the transition transmission device 4c is engaged with the second retaining device 321c to maintain relative motion. The second retaining device 321c can be a structure integrally formed with the self-rotation drive device 3c, or it can be a component separately provided from the self-rotation drive device 3c and mounted on the self-rotation drive device 3c. The second retaining device 321c can be a plane arranged along the second axis T8, a guide groove, or a pulley set arranged along the second axis T8. In this embodiment, the self-rotation drive device 3c includes a self-rotation drive gear 31c and a guide protrusion 32c integrally formed on the self-rotation drive gear 31c. The second sliding joint 42c is a second dovetail groove arranged along the second axis T8. The guide protrusion 32c is provided with a second dovetail slider arranged along the second axis T8. The second dovetail slider constitutes the second retaining device 321c. The second dovetail slider is slidably arranged in the second dovetail groove, so that the transition transmission device 4c can slide relative to the guide protrusion 32c in the direction of the second axis T8 and can rotate under the drive of the guide protrusion 32c when the self-rotation drive device 3c rotates. The second sliding joint 42c and the second retaining device 321c form a kinematic pair that allows the self-rotation drive device 3c and the transition transmission device 4c to maintain relative motion in the direction of the second axis T8. Secondly, the second retaining device 321c is used to define a reference for movement along the second axis T8. The above feature defines that the second sliding joint 42c moves along the second axis T8 with the second retaining device 321c as the movement reference. However, since the transition transmission device 4c and the self-rotation drive device 3c are in relative motion cooperation, it can actually be regarded as that the second sliding joint 42c and the second retaining device 321c are mutually defined references.

[0045] Second, a second specific embodiment (in this embodiment, the first axis T1 and the second axis T2 are perpendicular to each other, and the angle between them is 90°);

[0046] like Figure 1 and Figure 2As shown, an extruder utilizing an orbital-based self-rotation drive structure includes an orbital-based self-rotation drive structure 100 and an eccentric rotor volume pulsation deformation plasticizing extrusion device 200. The orbital-based self-rotation drive structure 100 comprises a housing 1, a power take-off shaft 2 disposed within the housing 1 and having an orbital motion trajectory, a self-rotation drive device 300, and a transition transmission device 4. Using a moving coordinate system consisting of a first axis T1, a second axis T2, and a Z axis as a reference (wherein the first axis T1 and the second axis T2 are respectively perpendicular to the Z axis, and when viewed along the Z axis, the angle between the first axis T1 and the second axis T2 is 90°), the power take-off shaft 2 extends along the Z axis, with one end of the power take-off shaft 2 extending from the housing 1 and connected to the rotor 201 of the eccentric rotor volume pulsation deformation plasticizing extrusion device 200. Left and right revolving drive gears (5, 5a) are also arranged in the housing 1. The rotation drive device 300 includes a rotation drive gear 3. The rotation drive gear 3 is located between the left and right revolving drive gears (5, 5a). The revolving drive gears (5, 5a) and the rotation drive gear 3 are rotatably arranged on the housing 1 through bearings (6, 61, 62). The power output shaft 2 is rotatably offset on the spokes of the revolving drive gear (5, 5a), and there is an offset between the rotation center line O1 of the power output shaft 2 and the rotation center line O2 of the revolving drive gear (5, 5a), thereby not only allowing the power output shaft 2 to rotate on the revolving drive gear (5, 5a), but also allowing the revolving drive gear (5, 5a) to drive the power output shaft 2 to revolve around the rotation center line O2 of the revolving drive gear (5, 5a), and the rotation center line O2 of the revolving drive gear (5, 5a) is consistent with the rotation center line O3 of the self-rotating drive gear 3. According to the above technical solution, the revolving axis O of the power output shaft 2 is consistent with the rotation center line O2 of the revolving drive gear (5, 5a) and the rotation center line O3 of the self-rotating drive gear 3. The housing 1 also includes a power input shaft 7, a gear set 71, a first power distribution shaft 72, and a second power distribution shaft 72a. The gear set 71 includes first transmission gears (71a, 71b) sleeved on and radially linked to the first power distribution shaft 72, and a second transmission gear 71c sleeved on and radially linked to the second power distribution shaft 72a. The power input shaft 7 is connected to the first power distribution shaft 72 and the second power distribution shaft 72a via a reduction gear set 73.The first power distribution shaft 72 is respectively connected to the revolution drive gears (5, 5a) through the first transmission gears (71a, 71b), and the second power distribution shaft 72a is respectively connected to the rotation drive gear 3 through the second transmission gear 71c. The gear set 71 allows the rotation of the power output shaft 2 to be opposite to the revolution direction but at the same speed.

[0047] like Figure 3 and Figure 4 As shown, the transition transmission device 4 is in the shape of a rectangular frame and thus has a first cavity 43. The first cavity 43 has first side cavity walls (41, 41a) arranged on the upper and lower sides and arranged respectively along the direction of the first axis T1, and the first side cavity walls (41, 41a) respectively constitute a first sliding joint. The transition transmission device 4 is also provided with cavity outer side surfaces (42, 42') arranged on the left and right sides and arranged respectively along the direction of the second axis T2, and the cavity outer side surfaces (42, 42') respectively constitute a second sliding joint. The power output shaft 2 includes a coupling shaft section 21, and the rotation center line O of the coupling shaft section 21 11 It is consistent with the rotation center line O1 of the power output shaft 2. The coupling shaft section 21 is rectangular and includes upper and lower shaft side walls (211, 211a), and the shaft side walls (211, 211a) are planes and are arranged not only along the first axis T1 direction, but also extending along the Z axis direction. The shaft side walls (211, 211a) respectively constitute first retaining devices, and the first retaining devices are used to define a reference for movement along the first axis direction T1. The coupling shaft section 21 is retained in the first cavity 43 of the transition transmission device 4, that is, the first retaining device is also retained in the first cavity 43 of the transition transmission device 4. The inner sides of the first side cavity walls (41, 41a) respectively abut against the shaft side walls (211, 211a) and are respectively connected to the shaft side walls (211, 211a) for transmission. In addition, the first side cavity wall (41, 41a) and the shaft side wall (211, 211a) also maintain relative motion cooperation in the direction of the first axis T1. According to the above technical solution, not only can the first side cavity wall (41, 41a) be used to provide a reference for the movement of the coupling shaft segment 21 along the direction of the first axis T7, but also, when the transition transmission device 4 rotates, the inner side edges of the first side cavity wall (41, 41a) can be used to respectively abut against the shaft side wall (211, 211a) to drive the coupling shaft segment 21 to rotate. In this way, the first mold cavity 43 is not only used to provide a placement space for the coupling shaft segment 21, but also used to provide a guide reference for the movement of the coupling shaft segment 21 along the direction of the first axis T1 or to transmit torsional torque by relying on its own mechanical structure.

[0048] The power output shaft 2 needs to perform not only rotation but also revolution, and in order to configure sufficient space for the revolution of the power output shaft 2, further, in the direction of the first axis T1, the first cavity 43 reserves a width L1 for the coupling shaft section 21 to move that is greater than the width L2 of the coupling shaft section 21 itself, and the width L1 is also greater than the width of the shaft side wall (211, 211a) itself so as not to hinder the revolution of the power output shaft 2. According to the above technical solution, the coupling shaft section 21 can not only transmit power with the transition transmission device 4, but also move in the first cavity 43 along the direction of the first axis T1. The width of the first cavity 43 in the direction of the first axis T1 is configured to provide a basic condition for not hindering the revolution of the power output shaft 2. It can be inferred in this way (refer to Figure 10 For understanding), the coupling shaft segment 21 moves relative to the transition transmission device 4 in the direction of the first axis T1 to form a first motion trajectory d1.

[0049] like Figure 3 and Figure 5As shown, a rectangular second cavity 31 is provided on the spoke 30 of the self-rotating drive gear 3. The rotation centerline of the second cavity 31 is consistent with the rotation centerline O3 of the self-rotating drive gear 3. The second cavity 31 has second side cavity walls (32, 32') arranged on the left and right sides and arranged along the second axis T2. The second side cavity walls (32, 32') are planes and are not only arranged along the second axis T2 but also extend along the Z-axis. The second side cavity walls (32, 32') respectively constitute second retaining devices, which are used to define a reference for movement along the second axis T2. The transition transmission device 4 is retained in the second cavity 31, that is, the second sliding joint is also retained in the second cavity 31. The outer side surfaces (42, 42') of the cavity of the transition transmission device 4 are respectively pressed against the inner side edges of the second side cavity walls (32, 32') and are transmission-connected with the second side cavity walls (32, 32'), and the outer side surfaces (42, 42') of the cavity and the second side cavity walls (32, 32') maintain relative motion cooperation in the direction of the second axis T2, that is, the self-rotating drive gear 3 is transmission-connected with the transition transmission device 4 and maintains relative motion cooperation in the direction of the second axis T2. According to the above technical solution, not only can the second side cavity walls (32, 32') be used to provide a reference for the transition transmission device 4 to move along the second axis T2, but also when the self-rotating drive gear 3 rotates, the structure in which the inner side edges of the second side cavity walls (32, 32') press against the outer side surfaces (42, 42') of the cavity can be used to drive the transition transmission device 4 to rotate. The second cavity 31 is not only used to provide a placement space for the intermediate transmission device 4, but also used to provide a guide reference for the intermediate transmission device 4 to move along the second axis T2 and transmit torsional torque by relying on its own mechanical structure.

[0050] The power output shaft 2 needs to perform not only self-rotation but also revolution. In order to configure sufficient space for the revolution of the power output shaft 2, further, in the direction of the second axis T2, the width L3 reserved for the transition transmission device 4 in the second cavity 31 is much larger than the width L4 of the transition transmission device 4 itself. The width L3 is also larger than the width of the outer surface (42, 42') of the cavity itself so as not to hinder the revolution of the power output shaft 2. According to the above technical solution, the transition transmission device 4 can not only transmit power with the self-rotation drive gear 3, but also move in the second cavity 31 along the direction of the second axis T2. The width of the second cavity 31 in the direction of the second axis T2 is configured to provide the basic condition for not hindering the revolution of the power output shaft 2. It can be inferred in this way (refer to Figure 10(For further understanding), the coupling shaft segment 21 can move relative to the self-rotating drive gear 3 in the direction of the second axis T2 to form a second motion trajectory d2. Combining the first motion trajectory d1 and the second motion trajectory d2, the coupling shaft segment 21 can move on a circular synthetic orbital trajectory with the orbital axis O as the center and R as the radius, wherein .

[0051] According to the above technical solution, if Figure 6 As shown, when the rotational kinetic energy is transmitted to the revolution drive gear (5, 5a) and the rotation drive gear 3 respectively through the power input shaft 7, since the outer side surfaces (42, 42') of the cavity of the transition transmission device 4 respectively press against the inner side edges of the second side cavity wall (32, 32') of the rotation drive gear 3, and the inner side edges of the first side cavity wall (41, 41a) of the transition transmission device 4 respectively press against the shaft side walls (211, 211a) of the coupling shaft section 21, the rotation of the transition transmission device 4 is performed in the clockwise direction ( Figure 6 The self-rotating driving gear 3 rotating in the direction indicated by the arrow S in the middle) can drive the combined shaft segment 21 to rotate in the clockwise direction around the rotation center line O1 through the transition transmission device 4. At the same time, driven by the revolution driving gear (5, 5a), the combined shaft segment 21 and the transition transmission device 4 maintain relative motion cooperation in the direction of the first axis T1, and the transition transmission device 4 and the self-rotating driving gear 3 maintain relative motion cooperation in the direction of the second axis T2, and the combined shaft segment 21 rotates in the counterclockwise direction ( Figure 6 The planet revolves in the direction indicated by the arrow N in the figure.

[0052] Thus, the coordination between the transition transmission device 4, the rotation drive device 300, and the power take-off shaft 2 allows the rotation of the power take-off shaft 2 to be driven by the rotation drive device 300 without hindering the revolution of the power take-off shaft 2. This allows for the selection of any desired rotational output torque within a continuous and stepless range by adjusting the coordination dimensions between the transition transmission device 4, the rotation drive device 300, and the power take-off shaft 2, respectively. This overcomes the existing patent CN201510407898.9, which states that the power take-off shaft's rotational output torque is directly proportional to the module m, a standardized parameter of the output planetary gears and the internal and external gears.

[0053] In addition, the power output shaft 2 is inevitably subjected to axial loads in specific applications. If the power output shaft 2 undergoes axial displacement under the action of the axial load, it is very likely to destroy the power transmission relationship between the power output shaft 2 and the transition transmission device 4. In view of this, a step 22 is further provided on the power output shaft 2, and one end face of the transition transmission device 4 rests on the step 22; a stopper 8 is also included, which is positioned on the self-rotating drive gear 3 by screws and presses against the other end face of the transition transmission device 4. In this way, the transition transmission device 4 is confined between the stopper 8 and the step 22 of the power output shaft 2, which is conducive to maintaining an effective power transmission relationship between the coupling shaft section 21 and the transition transmission device 4. In addition, the axial load borne by the power output shaft 2 can be transmitted to the self-rotating drive gear 3 through the step 22, the transition transmission device 4, and the stopper 8 in sequence, thereby improving the ability of the power output shaft 2 to resist axial loads.

[0054] Third, the third specific embodiment (in this embodiment, the angle between the first axis direction T3 and the second axis direction T4 is 80°);

[0055] like Figure 7The figure shows a schematic structural diagram of a third embodiment of a self-rotating drive structure 100a based on revolution. The self-rotating drive structure 100a shares a similar structure to the self-rotating drive structure 100. The key differences between them are discussed below: The self-rotating drive structure 100a includes a power output shaft 2a having an orbital motion trajectory, a self-rotating drive gear 3a, and an intermediate transmission device 4a. A trapezoidal second cavity 31a is provided on the spokes of the self-rotating drive gear 3a. The intermediate transmission device 4a is triangular and retained within the second cavity 31a. In both the first axial direction T3 and the second axial direction T4, the second cavity 31a provides a width greater than the width of the intermediate transmission device 4a itself, allowing the intermediate transmission device 4a to slide relative to the second cavity 31a not only in the first axial direction T3 but also in the second axial direction T4. A triangular first cavity 43a is provided on the transition transmission device 4a, and the power output shaft 2a is also triangular in shape and is retained in the first cavity 43a. In the first axial direction T3 and the second axial direction T4, the width of the first cavity 43a reserved for the power output shaft 2a to move is greater than the width of the power output shaft 2a itself, so that the power output shaft 2a can not only slide relative to the first cavity 43a in the first axial direction T3, but also in the second axial direction T4. Due to the above-mentioned coordination between the transition transmission device 4a, the self-rotating drive gear 3a, and the power output shaft 2a, the revolution of the power output shaft 2a is not hindered, and when the self-rotating drive gear 3a rotates, the power output shaft 2a can be driven to rotate by the transition transmission device 4a.

[0056] Fourth, the fourth specific embodiment (in this embodiment, the angle between the direction of the first axis T5 and the direction of the second axis T6 is 90°);

[0057] like Figure 8The fourth embodiment of a self-rotating drive structure 100b based on revolution is shown. This self-rotating drive structure 100b shares a similar structure to the self-rotating drive structure 100. The key differences between them are discussed below: The self-rotating drive structure 100b includes a power output shaft with an orbital motion trajectory, a self-rotating drive gear 3b, and an intermediate transmission device 4b. A second cavity 31b is defined on the spokes of the self-rotating drive gear 3b. This second cavity 31b has second side walls (32b, 32b') disposed on the left and right sides and arranged along the second axis T6. The intermediate transmission device 4b is retained within the second cavity 31b. The intermediate transmission device 4b includes a rod-shaped first sliding joint 41b and sliders (42b, 43b) disposed on the left and right ends of the first sliding joint 41b. These sliders (42b, 43b) each constitute a second sliding joint. The sliders (42b, 43b) abut against the inner side edges of the second side cavity walls (32b, 32b') and maintain relative motion engagement with the second side cavity walls (32b, 32b') in the direction of the second axis T6. The first retaining device of the coupling shaft segment 21b of the power output shaft is a cavity-shaped tunnel (obscured by the first sliding coupling portion 41b and not marked in the figure). The tunnel passes through the center of the coupling shaft segment 21b along the direction of the first axis T5. The centerline of the tunnel is located on the centerline O4 of the cross section of the coupling shaft segment 21b. The first sliding coupling portion 41b is inserted into the tunnel and maintains a sliding engagement in the direction of the first axis T5. According to the above technical solution, a sliding sleeve structure is formed between the first sliding joint 41b and the first retaining device, and the coupling shaft segment 21b can slide on the first sliding joint 41b along the first axial direction T5. When the self-rotating drive gear 3b rotates, the self-rotating drive gear 3b drives the transition transmission device 4b to rotate, and the rotating transition transmission device 4b can use the sliding sleeve structure to drive the coupling shaft segment 21b to rotate. Due to the above-mentioned cooperation between the transition transmission device 4b, the self-rotating drive gear 3b, and the power output shaft 2b, the revolution of the power output shaft 2b is not hindered. Moreover, when the self-rotating drive gear 3b rotates, the transition transmission device 4b can drive the power output shaft 2b to rotate.

Claims

1. A rotation drive method based on revolution, comprising a power output shaft having an orbital motion trajectory, a rotation drive device, and a transition transmission device, wherein the power output shaft extends along the Z axis, and from a transmission perspective, the transition transmission device is interposed between the power output shaft and the rotation drive device; characterized in that: The power output shaft is connected to the transition transmission device and maintained in relative motion coordination in the direction of the first axis. The transition transmission device is connected to the self-rotation drive device and maintained in relative motion coordination in the direction of the second axis. The first axis and the second axis are respectively perpendicular to the Z axis, and when viewed along the Z axis, the angle between the first axis and the second axis is not equal to zero. By utilizing the above-mentioned coordinated movement between the transition transmission device and the self-rotation drive device and the power output shaft, the self-rotation drive device can drive the power output shaft to rotate through the transition transmission device when the self-rotation drive device rotates without hindering the revolution of the power output shaft.

2. A rotation drive structure based on revolution, comprising a power output shaft having an orbital motion trajectory, a rotation drive device, and a transition transmission device, wherein the power output shaft extends along the Z axis, and from a transmission perspective, the transition transmission device is interposed between the power output shaft and the rotation drive device; characterized in that: The transition transmission device is connected to the power output shaft through transmission and maintains relative movement cooperation in the direction of the first axis, and can drive the power output shaft to rotate when the transition transmission device rotates; at the same time, the self-rotation drive device is connected to the transition transmission device through transmission and maintains relative movement cooperation in the direction of the second axis, and can drive the transition transmission device to rotate when the self-rotation drive device rotates; the first axis and the second axis are respectively perpendicular to the Z axis, and when viewed along the Z axis, the angle between the first axis and the second axis is not equal to zero; the transition transmission device is used for the above-mentioned cooperation with the self-rotation drive device and the power output shaft, and cooperates with the self-rotation drive device to drive the power output shaft to rotate without hindering the revolution of the power output shaft.

3. The rotation drive structure based on revolution according to claim 2, characterized in that: The transition transmission device is respectively provided with a first sliding joint arranged along the first axis direction and a second sliding joint arranged along the second axis direction. The power output shaft and the first sliding joint maintain relative movement cooperation in the first axis direction, and the self-rotation drive device and the second sliding joint maintain relative movement cooperation in the second axis direction.

4. The rotation drive structure based on revolution according to claim 3, characterized in that: The power output shaft includes a coupling shaft section, which is used to form a transmission connection with the transition transmission device, and the rotation center line of the coupling shaft section is consistent with the rotation center line of the power output shaft; the coupling shaft section includes a first retaining device, which is used to define a reference for movement along the first axis direction; the first sliding coupling part of the transition transmission device maintains relative movement and is engaged with the first retaining device.

5. The rotation drive structure based on revolution according to claim 4, characterized in that: The transition transmission device further includes a first cavity, and the first retaining device is retained in the first cavity.

6. The rotation-driven structure based on revolution according to claim 5, characterized in that: The first cavity has a first side cavity wall arranged along the first axis direction, the first side cavity wall constitutes the first sliding joint, and the inner side edge of the first side cavity wall rests on the first retaining device and maintains relative motion cooperation with the first retaining device.

7. The rotation drive structure based on revolution according to claim 5, characterized in that: In the direction of the first axis, the width of the first cavity reserved for the first retaining device to move is greater than the width of the first retaining device itself so as not to hinder the revolution of the power output shaft.

8. The rotation drive structure based on revolution according to claim 4, characterized in that: The first sliding joint of the transition transmission device is in the shape of a rod, and the first retaining device of the coupling shaft segment is a cavity-shaped tunnel. The tunnel passes through the center of the coupling shaft segment along the first axis direction, and the center line of the tunnel is located on the center line of the cross section of the coupling shaft segment. The first sliding joint is inserted into the tunnel and maintains a sliding fit in the direction of the first axis.

9. The rotation drive structure based on revolution according to any one of claims 3 to 8, characterized in that: The self-rotation drive device includes a second retaining device arranged along the second axis direction, and the second retaining device is used to define a reference for movement along the second axis direction; the second sliding joint on the transition transmission device maintains relative movement and is engaged with the second retaining device.

10. The rotation drive structure based on revolution according to claim 9, characterized in that: The self-rotation driving device further includes a second cavity, and the second sliding joint is retained in the second cavity.

11. The rotation-driven structure based on revolution according to claim 10, characterized in that: The second cavity has a second side cavity wall arranged along the second axis direction, the second side cavity wall constitutes the second retaining device, and the second sliding joint rests on the inner side edge of the second side cavity wall and maintains relative movement cooperation with the second side cavity wall.

12. The rotation-driven structure based on revolution according to claim 10, characterized in that: In the second axial direction, the width of the second cavity reserved for the second sliding joint to move is greater than the width of the second sliding joint itself so as not to hinder the revolution of the power output shaft.

13. The rotation drive structure based on revolution according to claim 10, characterized in that: The self-rotation drive device includes a self-rotation drive gear, the second cavity is arranged on the spoke of the self-rotation drive gear, the rotation center line of the second cavity is consistent with the rotation center line of the self-rotation drive gear, and the self-rotation drive gear and the transition transmission device are transmission-connected and maintain relative motion cooperation in the direction of the second axis.

14. The rotation drive structure based on revolution according to claim 9, characterized in that: The machine housing is also included. The self-rotation drive device and the power output shaft are arranged in the machine housing, and one end of the power output shaft extends out of the machine housing.

15. The rotation-driven structure based on revolution according to claim 14, characterized in that: The self-rotation drive device includes a self-rotation drive gear, and a step is also provided on the power output shaft, and one end face of the transition transmission device rests on the step; it also includes a stopper, which is positioned on the self-rotation drive gear by a screw and presses the other end face of the transition transmission device.

16. The rotation-driven structure based on revolution according to claim 14, characterized in that: There are also left and right revolving drive gears arranged in the machine housing, and the self-rotation drive device includes a self-rotation drive gear, which is located between the left and right revolving drive gears. The revolving drive gear and the self-rotation drive gear are respectively rotatably arranged on the machine housing through bearings; the power output shaft is rotatably offset on the spokes of the revolving drive gear so as to not only allow the power output shaft to rotate on the revolving drive gear, but also the revolving drive gear can drive the power output shaft to revolve around the rotation center line of the revolving drive gear, and the rotation center line of the revolving drive gear is consistent with the rotation center line of the self-rotation drive gear.

17. The rotation-driven structure based on revolution according to claim 16, characterized in that: It also includes a power input shaft, a gear set, and a power distribution shaft. The power input shaft is connected to the power distribution shaft through a reduction gear set, and the power distribution shaft is then connected to the revolution drive gear and the rotation drive gear through the gear set. The gear set allows the power output shaft to rotate in the opposite direction to the revolution direction but at the same speed.

18. An extruder using the self-rotation drive structure based on revolution according to any one of claims 2 to 17, characterized in that: It comprises the revolution-based self-rotation driving structure and the eccentric rotor volume pulsation deformation plasticizing extrusion device, wherein the power output shaft is connected to the rotor of the eccentric rotor volume pulsation deformation plasticizing extrusion device.

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