CN210600046U - Revolution-based rotation driving structure and applied extruder - Google Patents

Abstract

The revolution-based rotation driving structure comprises a power output shaft with a revolution motion track, a rotation driving device and a transition transmission device, wherein the power output shaft extends along the Z-axis direction, and the transition transmission device is arranged between the power output shaft and the rotation driving device when viewed from a transmission relation; the transition transmission device is in transmission connection with the power output shaft and keeps relative motion fit in the direction of a first axis, and when the transition transmission device rotates, the transition transmission device can drive the power output shaft to rotate; the beneficial technical effects of the utility model reside in that accessible adjustment transition transmission respectively with rotation drive arrangement, power output shaft between the cooperation size can select the rotation output torque of the arbitrary size of configuration in the scope of continuous stepless change.

Description

Revolution-based rotation driving structure and applied extruder

Technical Field

The invention relates to a mechanical driving method, in particular to a revolution-based rotation driving method, by which revolution torque and rotation torque can be output. The invention also relates to a structure for realizing the driving method and an extruder applying the driving method and the structure.

Background

In the field of machining, an actuating mechanism capable of simultaneously completing rotation and revolution motion is often required, for example, an apparatus for coaxially outputting rotation and revolution disclosed in patent CN201510407898.9, which includes a power input shaft, a power output shaft, a transition gear train and a K-H-V planetary gear train, wherein the power of the power input shaft is transmitted to the K-H-V planetary gear train through the transition gear train. The power input shaft comprises a main shaft and a crank shaft, the axis of the power output shaft is overlapped with the axis of the crank shaft of the power input shaft, the power output shaft revolves around the axis of the main shaft of the power input shaft, the revolution speed is equal to the rotation speed of the power input shaft, the main power of the power input shaft is superposed with the K-H-V planetary gear train with small tooth difference through the transition gear train, so that the power output shaft generates autorotation motion with constant speed and reverse direction with the power input shaft, and meanwhile, a thrust bearing which is coaxial with the power output shaft and rotates and revolves and a thrust bearing which is coaxial with the main shaft of the power input shaft are connected in series to bear axial load. The K-H-V planetary gear system with small tooth difference comprises an inner gear, an outer gear and an output planetary gear, wherein the power output shaft is arranged in a spoke hole of the output planetary gear, so that when the inner gear and the outer gear rotate, the power output shaft is driven to rotate through the output planetary gear. The rotation output torque of the power output shaft is in direct proportion to the module m of the output planetary gear and the inner and outer gears, and the module m is also in direct proportion to the eccentricity L between the output planetary gear and the inner and outer gears. Moreover, it cannot be ignored that the modulus m is a standardized parameter, which determines that the rotational output torque of the alternative arrangement of the power take-off shaft is also graded and cannot be graded.

Disclosure of Invention

The problem that the autorotation output torque of the power output shaft is graded is caused by the inherent characteristic of gear pair meshing transmission, cannot be solved by simply changing a gear structure, and must be completely new to change a transmission structure between an autorotation driving source and the power output shaft. In view of the above, the present invention provides a novel rotation driving method and structure that can rotate the power output shaft without interfering with the revolution of the power output shaft and can select and arrange the rotation output torque value of the power output shaft within a continuous and stepless range.

In view of the above, the present invention firstly proposes a rotation driving method based on revolution, which includes a power output shaft having a revolution motion trajectory, a rotation driving device and a transition transmission device, wherein the power output shaft is arranged to extend along a Z-axis direction, and the transition transmission device is interposed between the power output shaft and the rotation driving device when viewed from a transmission relation; the power output shaft and the transition transmission device are in transmission connection and keep in relative motion fit in a first axis direction, the transition transmission device and the rotation driving device are in transmission connection and keep in relative motion fit in a second axis direction, the first axis and the second axis are respectively perpendicular to the Z axis, and an included angle between the first axis and the second axis is not equal to zero when viewed along the Z axis direction; by utilizing the matching motion between the transition transmission device and the rotation driving device and between the transition transmission device and the power output shaft, the rotation driving device can drive the power output shaft to rotate through the transition transmission device when rotating while the revolution of the power output shaft is not hindered.

Secondly, the invention also provides a revolution-based rotation driving structure, which comprises a power output shaft with a revolution motion track, a rotation driving device and a transition transmission device, wherein the power output shaft extends along the Z-axis direction, and the transition transmission device is arranged between the power output shaft and the rotation driving device when viewed from a transmission relation; the transition transmission device is in transmission connection with the power output shaft and keeps relative motion fit in the direction of a first axis, and when the transition transmission device rotates, the transition transmission device can drive the power output shaft to rotate; meanwhile, the autorotation driving device is in transmission connection with the transition transmission device and keeps relative motion fit in the direction of a second axis, and when the autorotation driving device rotates, the transition transmission device can be driven to rotate; the first axis and the second axis are respectively perpendicular to the Z axis, and an included angle between the first axis and the second axis is not equal to zero when viewed along the Z axis direction; the transition transmission device is used for being matched with the rotation driving device and the power output shaft, and is matched with the rotation driving device to drive the power output shaft to rotate while the revolution of the power output shaft is not hindered.

The transition transmission device is provided with a first sliding joint part arranged along the first axial direction and a second sliding joint part arranged along the second axial direction, the power output shaft and the first sliding joint part are in relative motion fit in the first axial direction, and the rotation driving device and the second sliding joint part are in relative motion fit in the second axial direction.

The power output shaft comprises a combined shaft section, the combined shaft section is used for forming transmission connection with the transition transmission device, and the rotating center line of the combined shaft section is consistent with the rotating center line of the power output shaft; the combined shaft section comprises a first holding device which is used for defining a reference moving along the first axial direction; the first sliding interface of the transition gear remains in relative motion engagement with the first retaining device.

According to a further technical scheme, the transition transmission device further comprises a first cavity, and the first retaining device is retained in the first cavity.

According to a further technical scheme, the first cavity is provided with a first side cavity wall arranged along the first axial direction, the first side cavity wall forms the first sliding joint part, and the inner side edge of the first side cavity wall abuts against the first retaining device and keeps relative motion fit with the first retaining device.

In a further technical solution, in the first axial direction, a width of the first cavity reserved for the first holding device to be movable is larger than a width of the first holding device itself so as not to hinder revolution of the power output shaft.

The first sliding joint part of the transition transmission device is in a rod shape, the first holding device of the combined shaft section is a cavity-shaped tunnel, the tunnel penetrates through the center of the combined shaft section along the first axial direction, the center line of the tunnel is located on the center line of the cross section of the combined shaft section, and the first sliding joint part is inserted into the tunnel and keeps sliding fit in the first axial direction.

The rotation driving device may further include a second holding device disposed along the second axial direction, and the second holding device is configured to define a reference for movement along the second axial direction; the second sliding interface on the transition gear remains in relative motion engagement with the second retaining device.

In a further aspect, the rotation driving device may further include a second cavity, and the second sliding coupling portion may be held in the second cavity.

The second cavity has a second side cavity wall arranged along the second axial direction, the second side cavity wall forms the second holding device, and the second sliding joint part abuts against the inner side edge of the second side cavity wall and is in relative motion fit with the second side cavity wall.

In a further technical solution, in the second axial direction, a width of the second cavity reserved for the second sliding joint to be movable is far larger than a width of the second sliding joint so as not to hinder the revolution of the power output shaft.

The rotation driving device comprises a rotation driving gear, the second cavity is arranged on a spoke of the rotation driving gear, the rotation center line of the second cavity is consistent with the rotation center line of the rotation driving gear, and the rotation driving gear is in transmission connection with the transition transmission device and keeps relative motion fit in the direction of the second axis.

The further technical scheme can also be that the power transmission device further comprises a shell, the rotation driving device and the power output shaft are arranged in the shell, and one end of the power output shaft extends out of the shell. Therefore, the shell body becomes an outer protective layer of the rotation driving device and the power output shaft, so that the damage caused by the direct collision of foreign objects on the rotation driving device and the power output shaft can be avoided, impurities such as dust and metal particles can be shielded, the cleanliness and the transmission precision of the rotation driving device and the power output shaft can be maintained, and the service lives of the rotation driving device and the power output shaft can be effectively prolonged.

The power output shaft is inevitably subjected to axial load in specific application, if the power output shaft is axially displaced under the action of the axial load, the power transmission relationship between the power output shaft and the transition transmission device is possibly damaged, and in view of the further technical scheme, a step is further arranged on the power output shaft, and one end face of the transition transmission device is abutted against the step; the transmission device also comprises a stop block, wherein the stop block is positioned on the rotation driving gear through a screw and is pressed against the other end surface of the transition transmission device. In this way, the transition transmission device is limited between the stop block and the step of the power output shaft, and the axial load borne by the power output shaft can be transmitted to the self-rotation driving gear through the step, the transition transmission device and the stop block in sequence, so that the capacity of the power output shaft for resisting the axial load is improved.

The machine shell is internally provided with a left revolving driving gear and a right revolving driving gear, the revolving driving gear comprises a rotation driving gear, the rotation driving gear is positioned between the left revolving driving gear and the right revolving driving gear, and the revolving driving gear and the rotation driving gear are respectively and rotatably arranged on the machine shell through bearings; the power output shaft is rotatably offset on the spoke of the revolution driving gear so as to allow the power output shaft to rotate on the revolution driving gear, and the revolution driving gear can drive the power output shaft to revolve around the rotation center line of the revolution driving gear, and the rotation center line of the revolution driving gear is consistent with the rotation center line of the rotation driving gear. According to the technical scheme, the revolution axis of the power output shaft is consistent with the rotation center line of the revolution driving gear and the rotation center line of the rotation driving gear.

The power output shaft is connected with the power distribution shaft through a reduction gear set in a transmission mode, the power distribution shaft is connected with the revolution driving gear and the rotation driving gear through the gear set in a transmission mode, and the rotation of the power output shaft is opposite to the revolution direction but the rotating speed of the power output shaft is the same through the gear set.

Besides, the invention also provides an extruder applying the revolution-based rotation driving structure, which is characterized by comprising the revolution-based rotation driving structure and an eccentric rotor volume pulsating deformation plasticizing extrusion device, wherein the power output shaft is connected to a rotor of the eccentric rotor volume pulsating deformation plasticizing extrusion device.

According to the revolution-based rotation driving method and the revolution-based rotation driving structure, compared with the prior art, the invention has the beneficial technical effects that: because the transition transmission device is used for matching with the rotation driving device and the power output shaft, the transition transmission device is matched with the rotation driving device to drive the power output shaft to rotate while not interfering the revolution of the power output shaft, so that the rotation output torque with any size can be selected and configured in a continuous stepless range by adjusting the matching size between the transition transmission device and the rotation driving device and between the transition transmission device and the power output shaft, the predicament that the rotation output torque of the power output shaft and the module m which is a standardized parameter of the output planetary gear and the inner and outer gears are in a direct proportional relation in the prior patent CN201510407898.9 is eliminated, and the transition transmission device has the characteristics of simple structure and easy disassembly and replacement.

The present invention can be applied to a revolution-based rotation driving method, a revolution-based rotation driving structure, and an extruder used therefor, because of the above-described features and advantages.

Drawings

Fig. 1 is a schematic sectional structure view of an extruder to which a revolution-based rotation driving structure according to an embodiment of the present invention is applied;

fig. 2 is a schematic perspective view of the revolution-based rotation driving structure 100, in which the casing 1 is omitted;

FIG. 3 is a schematic cross-sectional view of the transition gear 4;

fig. 4 is a cross-sectional structural view of the coupling shaft segment 21 of the power take-off shaft 2;

fig. 5 is a side view schematically showing the structure of the rotation drive gear 3;

fig. 6 is a schematic view of the dynamic change of the revolution-based rotation driving structure 100, as viewed in a-a direction of fig. 1;

fig. 7 is a schematic sectional structure view of a revolution-based rotation driving structure 100a according to a third embodiment;

fig. 8 is a schematic sectional structure view of a revolution-based rotation driving structure 100b according to a fourth embodiment;

fig. 9 is a schematic sectional structure view of the revolution-based rotation driving structure 100c according to the basic embodiment, as viewed in the Z-axis direction;

fig. 10 is a schematic diagram of the revolution locus of the power output shaft 2 c.

Detailed Description

The revolution-based rotation driving method and structure and the extruder applied thereto to which the present invention is applied will be further described with reference to the accompanying drawings.

First, basic embodiment

As shown in fig. 9 and 10, a rotation driving method based on revolution includes a power output shaft 2c having a revolution motion track, a rotation driving device 3c, and a transition transmission device 4c, wherein the power output shaft 2c is arranged to extend along a Z-axis (not shown in fig. 9 and 10), and the transition transmission device 4c is arranged between the power output shaft 2c and the rotation driving device 3c when viewed from a transmission relation; the power output shaft 2c is in transmission connection with the transition transmission device 4c and is matched with the relative motion in the direction of a first axis T7, the transition transmission device 4c is in transmission connection with the rotation driving device 3c and is matched with the relative motion in the direction of a second axis T8, the first axis T7 and the second axis T8 are respectively perpendicular to the Z axis, and an included angle between the first axis T7 and the second axis T8 is not equal to zero when viewed in the Z axis direction, and certainly not equal to 180 degrees and 360 degrees; by the above-mentioned engagement motion between the transition transmission device 4c and the rotation driving device 3c and the power output shaft 2c, the rotation driving device 3c can drive the power output shaft 2c to rotate by the transition transmission device 4c when rotating, while the revolution of the power output shaft 2c is not hindered.

In addition, the present invention also provides a rotation driving structure 100c based on revolution. As shown in fig. 9 and 10, the rotation driving structure 100c includes a power output shaft 2c having a revolving motion trajectory, a rotation driving device 3c, and a transition transmission device 4c, the power output shaft 2c is arranged to extend in the Z-axis direction, and the transition transmission device 4c is interposed between the power output shaft 2c and the rotation driving device 3c as viewed from a transmission relationship; the transition transmission device 4c is in transmission connection with the power output shaft 2c and keeps relative motion fit in the direction of a first axis T7, and when the transition transmission device 4c rotates, the power output shaft 2c can be driven to rotate; meanwhile, the rotation driving device 3c is in transmission connection with the transition transmission device 4c and keeps relative motion fit in the direction of a second axis T8, and when the rotation driving device 3c rotates, the transition transmission device 4c can be driven to rotate; the first axis T7 and the second axis T8 are respectively perpendicular to the Z axis, and an included angle between the first axis T7 and the second axis T8 is not equal to zero when viewed along the Z axis direction; the transition transmission device 4c is used for matching with the rotation driving device 3c and the power output shaft 2c, and matching with the rotation driving device 3c to drive the power output shaft 2c to rotate while not interfering with the revolution of the power output shaft 2 c.

Wherein the power output shaft 2c has two motion forms respectively around the central axis O thereof₁A rotational autorotation movement and a revolution movement running around a revolution axis O, the central axis O₁Does not overlap the revolution axis O.

The above feature defines that the transitional transmission device 4c is a power transmission member between the power output shaft 2c and the rotation driving device 3c, and is used for transmitting the rotation torque of the rotation driving device 3c to the power output shaft 2c to drive the power output shaft 2c to rotate, wherein the transitional transmission device 4c is arranged between the power output shaft 2c and the rotation driving device 3c, as viewed from the transmission relation.

Wherein a 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 a change in position of the power output shaft 2c, and the first axis T7 and the second axis T8 respectively rotate about the Z axis on a plane perpendicular to the Z axis with rotation of the power output shaft 2 c. The first axis T7 and the second axis T8 form an included angle θ therebetween when viewed along the Z-axis direction, and the included angle θ may be 30 °, 60 °, 90 °, or the like, but is not 0 °, 180 °, 360 °, and in the present embodiment is 90 °.

The above feature defines that the rotation driving structure 100c is provided with a first moving space for moving the power output shaft 2c in the direction of the first axis T7, and the power output shaft 2c moves in the direction of the first axis T7 relative to the transition transmission device 4c to form a first moving track d 1. Next, the rotation driving device 3c is matched with the transition transmission device 4c to maintain the relative movement in the direction of the second axis T8, and the above feature defines that the rotation driving structure 100c is further provided with a second movable space for moving the transition transmission device 4c in the direction of the second axis T8, and the power output shaft 2c can actually move in the second movable space due to the movement of the power output shaft 2c relative to the transition transmission device 4c, and the power output shaft 2c moves relative to the rotation driving device 3c in the direction of the second axis T8 to form a second movement track d 2. As can be inferred from the above analysis, the movement locus of the power output shaft 2c on the plane defined by the first axis T7 and the second axis T8 is a circular synthetic revolution locus with the revolution axis O as the center and R as the radius, and R =

Thereby facilitating the revolution of the power output shaft 2 c.

In order to realize the power transmission between the transitional transmission device 4c and the power output shaft 2c and the rotation driving device 3c, the transitional transmission device 4c is further provided with a first sliding connection part 41c arranged along the first axis T7 and a second sliding connection part 42c arranged along the second axis T8, the power output shaft 2c and the first sliding connection part 41c are in relative motion fit in the first axis T7 direction, and the rotation driving device 3c and the second sliding connection part 42c are in relative motion fit in the second axis T8 direction. The first sliding coupling portion 41c may be a structure integrally formed with the transition transmission device 4c, or may be a member separately provided from the transition transmission device 4c and attached to the transition transmission device 4 c. The first sliding engagement portion 41c is configured with a guiding mechanism arranged in the direction of the first axis T7, but it is not excluded that the first sliding engagement portion 41c also has features arranged in other directions. For example, the first sliding-joint portion 41c may be a planar wall body that is arranged not only in the first axis T7 direction but also in the Z axis direction; the first sliding coupling portion 41c may be a three-dimensional structure such as a guide groove; it is also possible that said first sliding engagement portion 41c is a set of pulleys arranged along said first axis T7. In the present embodiment, the first sliding coupling portion 41c is a first dovetail groove arranged along the first axis T7. The second sliding coupling portion 42c and the first sliding coupling portion 41c have the same definition, and are not repeated herein. In the present embodiment, the second sliding coupling portion 42c is a second dovetail groove arranged along the second axis T8.

In order to realize the power transmission between the power output shaft 2c and the transition transmission device 4c, further, the power output shaft 2c includes a coupling shaft section 21c, the coupling shaft section 21c is used for forming a transmission connection with the transition transmission device 4c, and a rotation center line of the coupling shaft section 21c and a rotation center line O of the power output shaft 2c₁The consistency is achieved; the coupling shaft segment 21c comprises a first holding device 211c, and the first holding device 211c is used for defining a reference moving along the first axis T7; the first sliding engagement portion 41c of the transition gear 4c remains in a relative movement fit on the first retaining means 211 c. The first holding means 211c may be a structure integrally formed with the coupling shaft segment 21c, or may be a member separately provided from the coupling shaft segment 21c and attached to the coupling shaft segment 21 c. The first retaining device 211c may be a planar wall arranged along the first axis T7, a guide slot, or a pulley block arranged along the first axis T7. In this embodiment modeThe first sliding coupling portion 41c is a first dovetail groove arranged along the first axis T7, the first retaining device 211c is a first dovetail slider arranged along the first axis T7, and the first dovetail slider is slidably disposed in the first dovetail groove, so that the power output shaft 2c can slide relative to the transition gear 4c along the first axis T7 and can rotate under the driving of the transition gear 4c when the transition gear 4c rotates. The first sliding coupling portion 41c and the first retaining device 211c form a kinematic pair for keeping the coupling shaft segment 21c and the transition gear 4c in relative kinematic fit in the direction of the first axis T7. Next, the first holding device 211c is used for defining a reference moving along the first axis T7, and the above feature defines that the first sliding combination part 41c moves along the first axis T7 with the first holding device 211c as a moving reference. However, since the transition gear 4c and the coupling shaft segment 21c are in relative motion, the first sliding coupling portion 41c and the first retaining device 211c can be regarded as defining references.

In order to realize the power transmission between the rotation driving device 3c and the transition transmission device 4c, further, the rotation driving device 3c includes a second holding device 321c arranged along the second axis T8, and the second holding device 321c is used for defining a reference moving along the second axis T8; the second sliding engagement 42c on the transition gear 4c remains in a relative movement fit on the second holding means 321 c. The second holding device 321c may be a structure integrally formed with the rotation driving device 3c, or may be a member that is provided separately from the rotation driving device 3c and is attached to the rotation driving device 3 c. The second retaining means 321c may be a planar wall arranged along the second axis T8, a guide groove or a pulley block arranged along the second axis T8. In the present embodiment, the rotation driving device 3c includes a rotation driving gear 31c and a guide boss 32c integrally formed on the rotation driving gear 31 c. The second sliding coupling portion 42c is a second dovetail groove arranged along the second axis T8, and a second dovetail slider arranged along the second axis T8 is provided on the guide projection 32c, and constitutes the second holding device 321 c. The second dovetail slider is slidably disposed in the second dovetail groove, so that the transition transmission device 4c can slide relative to the guide protrusion 32c along the second axis T8, and can rotate under the driving of the guide protrusion 32c when the rotation driving device 3c rotates. The second sliding coupling portion 42c and the second holding device 321c constitute a kinematic pair in which the rotation driving device 3c and the transition transmission device 4c are held in relative motion and fit in the direction of the second axis T8. Next, the second holding device 321c is used for defining a reference of moving along the second axis T8, and the above feature defines that the second sliding coupling part 42c moves along the second axis T8 with the second holding device 321c as a moving reference. However, since the intermediate transmission device 4c and the rotation driving device 3c are relatively movably engaged with each other, the second sliding engagement portion 42c and the second holding device 321c may be regarded as a defining reference.

Second, second embodiment (in this embodiment, the first axis T1 and the second axis T2 are perpendicular to each other, and the included angle between them is 90 deg.)

As shown in fig. 1 and 2, an extruder using a revolution-based rotation driving structure includes a rotation driving structure 100 based on revolution and an eccentric rotor volume pulsation deformation plasticizing extrusion device 200. The revolution-based rotation driving structure 100 includes a housing 1, and a power output shaft 2 having a revolution motion track, a rotation driving device 300 and a transition transmission device 4 which are arranged in the housing 1. The power take-off shaft 2 is arranged to extend in the Z-axis direction, with reference to a movable coordinate system composed of a first axis direction T1, a second axis direction T2, and a Z-axis (wherein the first axis T1 and the second axis T2 are perpendicular to the Z-axis, respectively, and an angle between the first axis direction T1 and the second axis T2 is 90 ° as viewed in the Z-axis direction), and the power take-off shaft 2 is arranged to extend in the Z-axis directionOne end of the power output shaft 2 extends out of the shell 1 and is connected to a rotor 201 of the eccentric rotor volume pulse deformation plasticizing extrusion device 200. Revolution driving gears (5, 5 a) arranged on the left and the right are further arranged in the housing 1, the rotation driving device 300 comprises a rotation driving gear 3, the rotation driving gear 3 is positioned between the revolution driving gears (5, 5 a) arranged on the left and the right, and the revolution driving gear (5, 5 a) and the rotation driving gear 3 are respectively and rotatably arranged on the housing 1 through bearings (6, 61, 62). The power output shaft 2 is rotatably offset on the spokes of the revolution driving gear (5, 5 a), and the rotation center line O of the power output shaft 2₁And a rotation center line O of the revolution driving gear (5, 5 a)₂An offset distance exists between the two drive gears, so that the power output shaft 2 can rotate on the revolution drive gear (5, 5 a), and the revolution drive gear (5, 5 a) can drive the power output shaft 2 to rotate around the rotation center line O of the revolution drive gear (5, 5 a)₂Revolution, the revolution driving gear (5, 5 a) rotating central line O₂And a rotation center line O of the rotation driving gear 3₃And (5) the consistency is achieved. According to the technical scheme, the revolution axis O of the power output shaft 2 and the rotation center line O of the revolution driving gears (5, 5 a)₂And a rotation center line O of the rotation driving gear 3₃And (5) the consistency is achieved. Also included in the housing 1 are a power input shaft 7, a gear set 71, a first power distribution shaft 72 and a second power distribution shaft 72 a. The gear set 71 comprises first transmission gears (71 a and 71 b) sleeved on the first power distribution shaft 72 and radially linked with the first power distribution shaft, and further comprises a second transmission gear 71c sleeved on the second power distribution shaft 72a and radially linked with the second power distribution shaft. The power input shaft 7 is in transmission connection with the first power distribution shaft 72 and the second power distribution shaft 72a through a reduction gear set 73. The first power distribution shaft 72 is in transmission connection with the revolution driving gear (5, 5 a) through the first transmission gear (71 a, 71 b), the second power distribution shaft 72a is in transmission connection with the rotation driving gear 3 through the second transmission gear 71c, and the first power distribution shaft 72a is in transmission connection with the rotation driving gear (5, 5 a) through the second transmission gear 71cThe gear set 71 allows the power output shaft 2 to rotate in the opposite direction to the revolution but at the same speed.

As shown in fig. 3 and 4, the transition gear 4 has a rectangular frame shape and thus has a first cavity 43. The first cavity 43 has first side cavity walls (41, 41 a) arranged up and down and arranged along the first axis T1, respectively, and the first side cavity walls (41, 41 a) constitute first sliding joints, respectively. The transition transmission device 4 is further provided with cavity outer side faces (42, 42 ') which are arranged on the left and the right respectively and are arranged along the direction of the second axis T2, and the cavity outer side faces (42, 42') respectively form a second sliding joint part. The power output shaft 2 comprises a combined shaft section 21, and the rotating center line O of the combined shaft section 21₁₁And a rotation center line O of the power take-off shaft 2₁And (5) the consistency is achieved. The combined shaft segment 21 is rectangular and comprises shaft side walls (211, 211 a) which are arranged up and down, and the shaft side walls (211, 211 a) are planar wall bodies and are arranged along the direction of the first axis T1 and also extend along the direction of the Z axis. The shaft side walls (211, 211 a) respectively constitute first holding means for defining a reference for movement in the first axial direction T1. The coupling shaft portion 21 is held in the first cavity 43 of the transition gear 4, i.e. the first holding device is also held in the first cavity 43 of the transition gear 4. The inner side edges of the first side cavity walls (41, 41 a) respectively abut against the shaft side walls (211, 211 a) and are in transmission connection with the shaft side walls (211, 211 a). In addition, the first side cavity wall (41, 41 a) and the shaft side wall (211, 211 a) are also in relative motion fit in the direction of the first axis T1. According to the above technical solution, the first side cavity walls (41, 41 a) can be used not only to provide the reference for the combined shaft segment 21 to move along the first axis T7, but also to drive the combined shaft segment 21 to rotate when the transition transmission device 4 rotates by using the structure that the inner side edges of the first side cavity walls (41, 41 a) respectively abut against the shaft side walls (211, 211 a). In this way, the first cavity 43 is used not only for providing a placing space for the coupling shaft segment 21, but also for relying onIts own mechanical structure provides a guide reference or transfer torque for the combined shaft segment 21 to move in the direction of the first axis T1.

In order to allow the power output shaft 2 to perform not only the rotation movement but also the revolution movement, the first cavity 43 is provided with a width L1 in the direction of the first axis T1, which is larger than the width L2 of the coupling shaft segment 21, and the width L1 is larger than the width of the shaft side walls (211, 211 a) so as not to interfere with the revolution of the power output shaft 2, so that a sufficient space can be provided for the revolution of the power output shaft 2. According to the above-described aspect, the coupling shaft segment 21 can not only transmit power with the transition transmission device 4, but also move in the first cavity 43 along the first axis T1, and the width of the first cavity 43 in the first axis T1 direction is configured not to interfere with the revolution of the power output shaft 2 to provide a basic condition. As can be inferred (as can be understood with reference to fig. 10), the coupling shaft segment 21 moves relative to the transition gear 4 in the direction of the first axis T1 to form a first movement locus d 1.

As shown in fig. 3 and 5, the spoke 30 of the rotation driving gear 3 is provided with a rectangular second cavity 31. The rotation center line of the second cavity 31 coincides with the rotation center line O3 of the rotation drive gear 3. The second cavity 31 has a second side cavity wall (32, 32 ') which is divided left and right and arranged along the direction of the second axis T2, and the second side cavity wall (32, 32') is a plane wall body and is arranged along the direction of the second axis T2 and also extends along the direction of the Z axis. The second side chamber walls (32, 32') each constitute a second holding device for defining a reference for movement in the direction of the second axis T2. The transition gear 4 is held in the second cavity 31, i.e. the second sliding joint is also held in the second cavity 31. The outer side faces (42, 42 ') of the cavities of the transition transmission device 4 respectively abut against the inner side edges of the second side cavity walls (32, 32 ') and are in transmission connection with the second side cavity walls (32, 32 '), and the outer side faces (42, 42 ') of the cavities and the second side cavity walls (32, 32 ') are in relative motion fit in the direction of the second axis T2, namely the rotation driving gear 3 is in transmission connection with the transition transmission device 4 and is in relative motion fit in the direction of the second axis T2. According to the technical scheme, the second side cavity wall (32, 32 ') can be used for providing a reference for the transition transmission device 4 to move along the direction of the second axis T2, and the transition transmission device 4 can be driven to rotate by a structure that the inner side edge of the second side cavity wall (32, 32 ') abuts against the outer side surface (42, 42 ') of the cavity when the rotation driving gear 3 rotates. The second cavity 31 is not only used for providing a placing space for the transition transmission device 4, but also used for providing a guiding reference moving along the direction of the second axis T2 and transmitting a torsional moment for the transition transmission device 4 by means of a mechanical structure of the second cavity.

In order to provide sufficient space for the revolution of the power output shaft 2, the width L3 of the second cavity 31 reserved for the transition transmission device 4 to move is far greater than the width L4 of the transition transmission device 4 itself in the direction of the second axis T2, and the width L3 is also greater than the width of the outer side surface (42, 42') of the cavity itself so as not to hinder the revolution of the power output shaft 2. According to the above-described aspect, the transition transmission device 4 can not only transmit power to the rotation drive gear 3, but also move in the second cavity 31 in the direction of the second axis T2, and the width of the second cavity 31 in the direction of the second axis T2 is configured to provide a base condition without interfering with the revolution of the power output shaft 2. As can be understood from fig. 10, the coupling shaft segment 21 can move relative to the rotation drive gear 3 in the direction of the second axis T2 to form a second movement locus d 2. The first motion track d1 and the second motion track d2 are combined, and the combined shaft segment 21 can move on a circular synthetic revolution track with the revolution axis O as the center and R as the radius, wherein R =

。

According to the above technical solution, as shown in fig. 6, when the rotational kinetic energy is transmitted to the revolution driving gear (5, 5 a) and the rotation driving gear 3 through the power input shaft 7, since the outer side surfaces (42, 42 ') of the cavities of the transition transmission device 4 respectively abut against the inner sides of the second side cavity walls (32, 32') of the rotation driving gear 3, the inner sides of the first side cavity walls (41, 41 a) of the transition transmission device 4 respectively abut against the shaft side walls (211, 211 a) of the coupling shaft segment 21, and the rotation driving gear 3 rotating in the clockwise direction (the direction indicated by the arrow S in fig. 6) can drive the coupling shaft segment 21 to rotate around the rotation center line O through the transition transmission device 4₁Rotating in the clockwise direction. Meanwhile, under the driving of the revolution driving gear (5, 5 a), the coupling shaft segment 21 and the transition transmission device 4 are in relative motion fit in the direction of the first axis T1, and the transition transmission device 4 and the rotation driving gear 3 are in relative motion fit in the direction of the second axis T2, and the coupling shaft segment 21 revolves in a counterclockwise direction (the direction indicated by the arrow N in fig. 6) on a circular synthetic revolution track with the revolution axis O as the center and R as the radius.

As can be seen, the engagement between the transition transmission device 4, the rotation driving device 300 and the power output shaft 2 engages with the rotation driving device 300 to drive the power output shaft 2 to rotate while not interfering with the revolution of the power output shaft 2. In this way, the matching size between the transition transmission device 4 and the rotation driving device 300 and between the transition transmission device and the power output shaft 2 can be adjusted to select and configure the rotation output torque with any size in the continuous stepless range, and the difficulty that the rotation output torque of the power output shaft and the module m, which is the standardized parameter of the output planetary gear and the internal and external gears, are in direct proportional relation in the prior patent CN201510407898.9 is eliminated.

In addition, the power output shaft 2 is inevitably subjected to axial load in specific applications, and if the power output shaft 2 is axially displaced under the action of the axial load, the power transmission relationship between the power output shaft 2 and the transition transmission device 4 is possibly damaged, and in view of this, a step 22 is further arranged on the power output shaft 2, and one end face of the transition transmission device 4 is abutted against the step 22; the automatic transmission device also comprises a stop block 8, wherein the stop block 8 is positioned on the self-rotation driving gear 3 through a screw and is pressed against the other end surface of the transition transmission device 4. In this way, the transition transmission device 4 is limited between the stopper 8 and the step 22 of the power output shaft 2, which is beneficial to keeping the effective power transmission relationship between the combined shaft section 21 and the transition transmission device 4, and in addition, the axial load borne by the power output shaft 2 can be transmitted to the rotation driving gear 3 through the step 22, the transition transmission device 4 and the stopper 8 in sequence, thereby being beneficial to improving the capability of the power output shaft 2 for resisting the axial load.

Third, the third embodiment (the angle between the first axial direction T3 and the second axial direction T4 is 80 degree in this embodiment)

As shown in fig. 7, a schematic structural diagram of a rotation driving structure 100a based on revolution according to a third embodiment is adopted, and the rotation driving structure 100a has a similar structure to the rotation driving structure 100, and the following focuses on the main differences: the rotation driving structure 100a includes a power output shaft 2a having a revolution motion trajectory, a rotation driving gear 3a, and a transition transmission device 4 a. A trapezoidal second cavity 31a is provided on the spoke of the rotation drive gear 3a, and the transition transmission device 4a is triangular in shape and held in the second cavity 31 a. In the first axial direction T3 and the second axial direction T4, the width of the second cavity 31a which is reserved for the movement of the transition gear 4a is greater than the width of the transition gear 4a itself, so that the transition gear 4a can slide not only in the first axial direction T3 but also in the second axial direction T4 relative to the second cavity 31 a. The intermediate transmission 4a is provided with a first cavity 43a having a triangular shape, and the power take-off shaft 2a is also held in the first cavity 43a having a triangular shape. In the first axial direction T3 and the second axial direction T4, the first cavity 43a is respectively reserved for the power take-off shaft 2a to move by a width greater than the width of the power take-off shaft 2a itself, so that the power take-off shaft 2a can slide not only in the first axial direction T3 but also in the second axial direction T4 relative to the first cavity 43 a. Since the engagement is provided between the intermediate transmission device 4a and the rotation drive gear 3a and the power output shaft 2a, the rotation drive gear 3a does not interfere with the revolution of the power output shaft 2a, and the power output shaft 2a can be driven to rotate by the intermediate transmission device 4a when the rotation drive gear 3a rotates.

Fourth, the fourth embodiment (the included angle between the first axis T5 and the second axis T6 is 90 degree in this embodiment)

As shown in fig. 8, a rotation driving structure 100b based on revolution according to the fourth embodiment is adopted, and the rotation driving structure 100b has a similar structure to the rotation driving structure 100, and the main difference points are discussed in detail below: the rotation driving structure 100b includes a power output shaft having a revolution motion trajectory, a rotation driving gear 3b, and a transition transmission device 4 b. A second cavity 31b is provided on the spoke of the rotation driving gear 3b, the second cavity 31b having second side cavity walls (32 b, 32 b') that are left and right divided and arranged in the direction of the second axis T6. The transition gear 4b is held in the second cavity 31 b. The transition transmission device 4b comprises a first sliding joint part 41b in a rod shape and sliding blocks (42 b, 43 b) arranged at the left end and the right end of the first sliding joint part 41b, and the sliding blocks (42 b, 43 b) respectively form a second sliding joint part. The slider (42 b, 43 b) rests against the inner side of the second lateral cavity wall (32 b, 32b ') and is in relative kinematic engagement with the second lateral cavity wall (32 b, 32 b') in the direction of the second axis T6. The first retaining means of the coupling portion 21b of the power take-off shaft is a tunnel (not shown) in the form of a cavity, which passes through in the direction of the first axis T5 (obscured by the first sliding coupling portion 41 b)The center line of the tunnel is located at the center line O of the cross section of the combined shaft section 21b₄The first sliding coupling portion 41b is inserted into the tunnel and maintains a sliding fit in the direction of the first axis T5. According to the above-described aspect, a sliding insertion structure is formed between the first sliding coupling portion 41b and the first holding device, the coupling shaft segment 21b is slidable in the first axial direction T5 on the first sliding coupling portion 41b, and when the rotation driving gear 3b rotates, the rotation driving gear 3b rotates the transition transmission device 4b, and the rotating transition transmission device 4b can drive the coupling shaft segment 21b to rotate by the sliding insertion structure. Since the engagement is provided between the intermediate transmission device 4b and the rotation drive gear 3b and the power output shaft 2b, the rotation of the power output shaft 2b is not hindered, and the rotation drive gear 3b can drive the power output shaft 2b to rotate by the intermediate transmission device 4b when rotating.

Claims (17)

1. The rotation driving structure based on revolution comprises a power output shaft with a revolution motion track, a rotation driving device and a transition transmission device, wherein the power output shaft extends along the Z-axis direction, and the transition transmission device is arranged between the power output shaft and the rotation driving device when viewed from a transmission relation; the transition transmission device is in transmission connection with the power output shaft and keeps relative motion fit in the direction of a first axis, and when the transition transmission device rotates, the transition transmission device can drive the power output shaft to rotate; meanwhile, the autorotation driving device is in transmission connection with the transition transmission device and keeps relative motion fit in the direction of a second axis, and when the autorotation driving device rotates, the transition transmission device can be driven to rotate; the first axis and the second axis are respectively perpendicular to the Z axis, and an included angle between the first axis and the second axis is not equal to zero when viewed along the Z axis direction; the transition transmission device is used for being matched with the rotation driving device and the power output shaft, and is matched with the rotation driving device to drive the power output shaft to rotate while the revolution of the power output shaft is not hindered.

2. The revolution-based rotation driving structure according to claim 1, wherein the transition transmission device is provided with a first sliding coupling portion arranged in the first axial direction and a second sliding coupling portion arranged in the second axial direction, respectively, the power output shaft and the first sliding coupling portion are in relative-movement engagement in the first axial direction, and the rotation driving device and the second sliding coupling portion are in relative-movement engagement in the second axial direction.

3. The revolution-based rotation driving structure as claimed in claim 2, wherein the power take-off shaft comprises a coupling shaft section for forming a transmission connection with the transition transmission device, and a rotation center line of the coupling shaft section is coincident with a rotation center line of the power take-off shaft; the combined shaft section comprises a first holding device which is used for defining a reference moving along the first axial direction; the first sliding interface of the transition gear remains in relative motion engagement with the first retaining device.

4. The revolution-based rotation driving structure as claimed in claim 3, wherein the transition transmission means further comprises a first cavity, and the first holding means is held in the first cavity.

5. The revolution-based rotation driving structure as claimed in claim 4, wherein 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 an inner side edge of the first side cavity wall abuts against the first holding device and is in relative motion fit with the first holding device.

6. The revolution based rotation driving structure as claimed in claim 4, wherein the first cavity is reserved for the first holding means to be movable by a width larger than a width of the first holding means itself in the first axial direction so as not to interfere with the revolution of the power output shaft.

7. The revolution-based rotation driving structure as claimed in claim 3, wherein the first sliding coupling portion of the transition transmission device is formed in a rod shape, the first holding device of the coupling shaft section is formed in a cavity-shaped tunnel penetrating the center of the coupling shaft section in the first axial direction, the center line of the tunnel is located on the center line of the cross section of the coupling shaft section, and the first sliding coupling portion is inserted into the tunnel and held in sliding engagement in the first axial direction.

8. The revolution-based rotation driving structure as claimed in any one of claims 2 to 7, wherein the rotation driving means includes a second holding means arranged in the second axial direction for defining a reference for movement in the second axial direction; the second sliding interface on the transition gear remains in relative motion engagement with the second retaining device.

9. The revolution-based rotation driving structure as claimed in claim 8, wherein the rotation driving means further comprises a second cavity, and the second sliding coupling part is held in the second cavity.

10. The revolution-based rotation driving structure as claimed in claim 9, wherein the second cavity has a second side wall arranged along the second axial direction, the second side wall constitutes the second holding means, and the second sliding connection part abuts against an inner side edge of the second side wall and is held in relative motion engagement with the second side wall.

11. The revolution based rotation driving structure as claimed in claim 9, wherein the second cavity is reserved for the second sliding engagement portion to be movable by a width much larger than a width of the second sliding engagement portion itself in the second axis direction so as not to interfere with the revolution of the power output shaft.

12. The revolution-based rotation driving structure as claimed in claim 9, wherein the rotation driving means comprises a rotation driving gear, the second cavity is provided on a spoke of the rotation driving gear, a rotation center line of the second cavity coincides with a rotation center line of the rotation driving gear, and the rotation driving gear is in transmission connection with the transition transmission means and maintains relative motion fit in the direction of the second axis.

13. The revolution-based rotation driving structure as claimed in claim 8, further comprising a housing, wherein the rotation driving means, the power output shaft are disposed in the housing, and one end of the power output shaft extends out of the housing.

14. The revolution-based rotation driving structure as claimed in claim 13, wherein the rotation driving means comprises a rotation driving gear, a step is further provided on the power output shaft, and one end face of the transition transmission means abuts against the step; the transmission device also comprises a stop block, wherein the stop block is positioned on the rotation driving gear through a screw and is pressed against the other end surface of the transition transmission device.

15. The revolution-based rotation driving structure as claimed in claim 13, wherein a left and a right arranged revolution driving gears are further arranged in the casing, the rotation driving means comprises a rotation driving gear between the left and the right arranged revolution driving gears, the revolution driving gear and the rotation driving gear are rotatably provided on the casing through bearings, respectively; the power output shaft is rotatably offset on the spoke of the revolution driving gear so as to allow the power output shaft to rotate on the revolution driving gear, and the revolution driving gear can drive the power output shaft to revolve around the rotation center line of the revolution driving gear, and the rotation center line of the revolution driving gear is consistent with the rotation center line of the rotation driving gear.

16. The revolution-based rotation driving structure as claimed in claim 15, further comprising a power input shaft, a gear set, and a power distribution shaft, wherein the power input shaft is in transmission connection with the power distribution shaft through a reduction gear set, the power distribution shaft is in transmission connection with the revolution driving gear and the rotation driving gear through the gear set, respectively, and the gear set enables the rotation direction of the power output shaft to be opposite to the revolution direction, but the rotation speed of the power output shaft to be the same.

17. An extruder using the revolution-based rotation driving structure of any one of claims 1 to 16, comprising the revolution-based rotation driving structure and an eccentric rotor volume pulsation deformation plasticizing extrusion device, wherein the power output shaft is connected to a rotor of the eccentric rotor volume pulsation deformation plasticizing extrusion device.

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