CN116792358A - Rotary driving mechanism, arm support and engineering machinery - Google Patents
Rotary driving mechanism, arm support and engineering machinery Download PDFInfo
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- CN116792358A CN116792358A CN202210259497.3A CN202210259497A CN116792358A CN 116792358 A CN116792358 A CN 116792358A CN 202210259497 A CN202210259497 A CN 202210259497A CN 116792358 A CN116792358 A CN 116792358A
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- annular
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- 230000007246 mechanism Effects 0.000 title claims abstract description 33
- 238000010276 construction Methods 0.000 claims description 3
- 241000405098 Champsodontidae Species 0.000 abstract description 4
- 230000005540 biological transmission Effects 0.000 abstract description 4
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 238000005299 abrasion Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000004880 explosion Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 230000036544 posture Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
- B66C23/62—Constructional features or details
- B66C23/64—Jibs
- B66C23/68—Jibs foldable or otherwise adjustable in configuration
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
- B66C23/62—Constructional features or details
- B66C23/64—Jibs
- B66C23/70—Jibs constructed of sections adapted to be assembled to form jibs or various lengths
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04G—SCAFFOLDING; FORMS; SHUTTERING; BUILDING IMPLEMENTS OR AIDS, OR THEIR USE; HANDLING BUILDING MATERIALS ON THE SITE; REPAIRING, BREAKING-UP OR OTHER WORK ON EXISTING BUILDINGS
- E04G21/00—Preparing, conveying, or working-up building materials or building elements in situ; Other devices or measures for constructional work
- E04G21/02—Conveying or working-up concrete or similar masses able to be heaped or cast
- E04G21/04—Devices for both conveying and distributing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
- F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H27/00—Step-by-step mechanisms without freewheel members, e.g. Geneva drives
- F16H27/02—Step-by-step mechanisms without freewheel members, e.g. Geneva drives with at least one reciprocating or oscillating transmission member
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Architecture (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Hydraulic Motors (AREA)
- Actuator (AREA)
Abstract
The invention relates to the field of arm frames and discloses a rotary driving mechanism, an arm frame and engineering machinery, wherein the rotary driving mechanism comprises an annular piston (10) and a stator, the annular piston (10) is provided with a piston tooth part with a protruding bent tooth surface and a piston tooth part with an inclined flat tooth surface, the stator is provided with a stator tooth part with a protruding bent tooth surface and a stator tooth part with an inclined flat tooth surface, and the annular piston (10) can be driven to axially move relative to the stator. By combining the engagement of the curved tooth surface with the engagement of the flat tooth surface, the above-mentioned technical proposal can ensure smooth transmission in the initial engagement stage, has smaller noise, and can convert axial movement into uniform rotation in the subsequent engagement stage, thereby providing more stable torque output.
Description
Technical Field
The invention relates to the field of arm frames, in particular to a rotary driving mechanism, an arm frame and engineering machinery.
Background
The arm support is usually formed by hinging a plurality of arm sections, and is unfolded and folded by driving the arm cylinders of each section, the magnitude of the relative rotation angle between two adjacent arm sections is a key factor influencing the flexibility and the working range of the arm support, and the larger the relative rotation angle between two adjacent arm sections is, the larger the flexibility and the working range of the arm support are, and otherwise, the smaller the relative rotation angle between the two adjacent arm sections is.
At present, the maximum relative rotation angle between two adjacent arm sections of most arm support systems does not exceed 220 degrees, and sometimes the distribution condition in a complex construction environment is difficult to meet, and particularly when the arm support systems need to avoid obstacles, the arm support systems are difficult to be unfolded into the required postures due to the limited relative rotation angle. In addition, the arm joint connecting mode formed by hinging the oil cylinder and the bent plate can enable the movement mode of the arm support to be single when the arm support is unfolded, and the arm joint can only be unfolded clockwise or anticlockwise; furthermore, when the relative rotation angle of the arm sections is large, if the arm sections are required to be retracted, the arm sections can only rotate in opposite directions by a very large angle, so that the flexibility and the working efficiency of the arm support are greatly reduced.
In addition, the relative angular velocity of the rotation between the arm sections is not in direct proportion to the stroke of the oil cylinder, the angular velocity of the arm sections is continuously changed along with the continuous change of the relative rotation angle, and an amplifying effect is formed at the tail end due to the fact that the arm sections are long, and the fluctuation can obviously reduce the stability and accuracy of the tail end of the arm frame.
Disclosure of Invention
The invention aims to provide a rotary driving mechanism to solve the problems of uneven torque output and non-constant rotating speed.
In order to achieve the above object, an aspect of the present invention provides a rotary drive mechanism including an annular piston provided with a piston tooth portion having a protruding curved tooth surface and a piston tooth portion having an inclined flat tooth surface, and a stator provided with a stator tooth portion having a protruding curved tooth surface and a stator tooth portion having an inclined flat tooth surface, the annular piston being capable of being driven to move axially with respect to the stator, and the annular piston being engaged with the stator tooth portion having the protruding curved tooth surface by the piston tooth portion having the protruding curved tooth surface and then engaged with the stator tooth portion having the inclined flat tooth surface by the piston tooth portion having the inclined flat tooth surface to drive the annular piston to rotate circumferentially.
Alternatively, the stator includes a first stator and a second stator in the shape of a ring, and the annular piston is disposed between the first stator and the second stator.
Optionally, the first end in the axial direction of the annular piston is provided with a first piston tooth part and a second piston tooth part, the second end in the axial direction is provided with a third piston tooth part and a fourth piston tooth part, the first stator is provided with a first stator tooth part capable of being meshed with the first piston tooth part and a second stator tooth part capable of being meshed with the second piston tooth part, the second stator is provided with a third stator tooth part capable of being meshed with the third piston tooth part and a fourth stator tooth part capable of being meshed with the fourth piston tooth part, the first piston tooth part and the first stator tooth part respectively have protruding bent tooth surfaces, the second piston tooth part and the second stator tooth part respectively have inclined flat tooth surfaces, the third piston tooth part and the third stator tooth part respectively have protruding bent tooth surfaces, the fourth piston tooth part and the fourth stator tooth part respectively have inclined flat tooth surfaces,
wherein the annular piston is capable of being driven to axially reciprocate, wherein the first piston tooth portion is engaged with the first stator tooth portion, then the second piston tooth portion is engaged with the second stator tooth portion, the third piston tooth portion is engaged with the third stator tooth portion, then the fourth piston tooth portion is engaged with the fourth stator tooth portion, thereby pushing the annular piston to rotate.
Optionally, the first piston tooth, the first stator tooth, the third piston tooth, and the third stator tooth each have involute tooth surfaces.
Alternatively, the first and second piston teeth are located radially inward and outward, respectively, and the third and fourth piston teeth are located radially inward and outward, respectively.
Alternatively, the first piston tooth portion and the second piston tooth portion are in one-to-one correspondence and the center lines are aligned, the first stator tooth portion and the second stator tooth portion are in one-to-one correspondence and the center lines are aligned, the third piston tooth portion and the fourth piston tooth portion are in one-to-one correspondence and the center lines are aligned, and the third stator tooth portion and the fourth stator tooth portion are in one-to-one correspondence and the center lines are aligned.
Optionally, the centerlines of the first and second stator teeth are offset from the centerlines of the third and fourth stator teeth, and the centerlines of the first and second piston teeth are aligned with the centerlines of the third and fourth piston teeth.
Optionally, the distance between the tooth tips of the first and second piston teeth and the tooth tips of the third and fourth piston teeth is greater than the distance between the tooth tips of the first and second stator teeth and the tooth tips of the third and fourth stator teeth, and less than the distance between the tooth tips of the first and second stator teeth and the tooth roots of the third and fourth stator teeth, and less than the distance between the tooth roots of the first and second stator teeth and the tooth tips of the third and fourth stator teeth.
Alternatively, the rotary driving mechanism includes two sets of the first stator, the second stator and the annular piston which are axially arranged, the first stator and the second stator of the two sets are relatively fixed, and the two annular pistons are relatively fixed in the circumferential direction and can axially move relatively.
Alternatively, the centerlines of the first piston teeth of the two annular pistons are offset.
Alternatively, the rotary drive mechanism includes an inner ring to which two of the annular pistons are axially slidably mounted, and both of the annular pistons are circumferentially fixed relative to the inner ring.
In addition, the invention also provides a cantilever crane, wherein the cantilever crane is provided with the rotary driving mechanism.
In addition, the invention also provides engineering machinery, wherein the engineering machinery is provided with the arm support.
By combining the engagement of the curved tooth surface with the engagement of the flat tooth surface, the above-mentioned technical proposal can ensure smooth transmission in the initial engagement stage, has smaller noise, and can convert axial movement into uniform rotation in the subsequent engagement stage, thereby providing more stable torque output.
Drawings
FIG. 1 is a partial schematic view of a rotary drive mechanism according to an embodiment of the present invention;
FIG. 2 is an explosion of a rotary drive mechanism according to an embodiment of the present invention;
FIG. 3 is a perspective view of an annular piston according to an embodiment of the present invention;
FIG. 4 is a schematic view of the configuration of the annular piston in cooperation with a stator according to an embodiment of the present invention;
FIG. 5 is a diagram of the process of mating the teeth of the annular piston with the teeth of the stator according to an embodiment of the present invention;
fig. 6 and 7 are process diagrams of the annular piston rotating in two different directions relative to the stator, respectively.
Description of the reference numerals
10-annular piston, 11-first piston tooth, 12-second piston tooth, 13-third piston tooth, 14-fourth piston tooth, 20-second stator, 21-first stator tooth, 22-second stator tooth, 30-second stator, 31-third stator tooth, 32-fourth stator tooth, 40-inner ring, 50-end cap.
Detailed Description
The following describes specific embodiments of the present invention in detail with reference to the drawings. It should be understood that the detailed description and specific examples, while indicating and illustrating the invention, are not intended to limit the invention.
The present invention provides a rotary drive mechanism, wherein the rotary drive mechanism includes an annular piston 10 provided with a piston tooth portion having a protruding curved tooth surface and a piston tooth portion having an inclined flat tooth surface, and a stator provided with a stator tooth portion having a protruding curved tooth surface and a stator tooth portion having an inclined flat tooth surface, the annular piston 10 being capable of being driven to axially move relative to the stator, and the annular piston 10 being engaged with the stator tooth portion having the protruding curved tooth surface by the piston tooth portion having the protruding curved tooth surface and then engaged with the stator tooth portion having the inclined flat tooth surface by the piston tooth portion having the inclined flat tooth surface to drive the annular piston 10 to circumferentially rotate.
One of the tooth surfaces of the annular piston 10 is a curved tooth surface and is in a protruding shape, the other tooth surface is a plane, the tooth surface of one tooth of the stator is a curved tooth surface and protrudes outward, the other tooth surface is a plane, the curved tooth surface of the annular piston 10 is matched with the curved tooth surface of the stator, and the plane tooth surface of the annular piston 10 is matched with the plane tooth surface of the stator.
The tooth surface refers to a surface where two tooth portions are engaged with each other when they are engaged with each other. The axial direction refers to the axial direction of the annular piston 10, and the circumferential direction is also the circumferential direction of the annular piston 10.
In particular, the annular piston 10 may be driven to move axially, for example, by hydraulic pressure, pneumatic pressure, or the like, so that the teeth at both ends thereof are brought into and out of engagement with the teeth of the stator, respectively, the teeth on the stator being slightly offset from the teeth of the annular piston 10 during engagement of the two teeth with each other, the teeth on the stator being capable of guiding the teeth on the annular piston 10 to move relatively circumferentially so that the teeth of the annular piston 10 move into alignment with the teeth roots of the stator teeth to effect rotation of the annular piston 10 relative to the stator.
Referring to fig. 5, when the annular piston 10 is meshed with a stator (for example, the first stator 20), the initial meshing of the annular piston 10 and the first stator 20 is realized by the tooth meshing of a curved tooth surface, namely, a conventional tooth structure, and the design can enable abrasion between tooth parts to be less, transmission to be stable, and has the advantages of labor saving, low durable noise and the like, and of course, even if the axial relative movement of the annular piston 10 and the stator is uniform, the circumferential relative movement caused by meshing is non-uniform; then, the second piston tooth 12 meshes with the second stator tooth 22, and the two teeth are shaped structures of different conventional teeth, i.e. tooth surfaces are planes, and an included angle is formed between the planes and the axial direction (or the center line of the teeth), so that when the axial relative movement is uniform, the circumferential movement of the annular piston 10 relative to the first stator 20 is also uniform, i.e. uniform rotation is realized.
The stator includes a first stator 20 and a second stator 30 having a ring shape, and an annular piston 10 is disposed between the first stator 20 and the second stator 30. The annular piston 10 can axially move between the first stator 20 and the second stator 30, and the annular piston 10 is driven to circumferentially rotate through the meshing engagement of the teeth, so that continuous rotation is realized.
Specifically, the first end in the axial direction of the annular piston 10 is provided with a first piston tooth 11 and a second piston tooth 12, and the second end in the axial direction is provided with a third piston tooth 13 and a fourth piston tooth 14, the first stator 20 is provided with a first stator tooth 21 capable of engaging with the first piston tooth 11 and a second stator tooth 22 capable of engaging with the second piston tooth 12, the second stator 30 is provided with a third stator tooth 31 capable of engaging with the third piston tooth 13 and a fourth stator tooth 32 capable of engaging with the fourth piston tooth 14, the first piston tooth 11 and the first stator tooth 21 have respectively protruding curved tooth surfaces, the second piston tooth 12 and the second stator tooth 22 have respectively inclined flat tooth surfaces, the third piston tooth 13 and the third stator tooth 31 have respectively protruding curved tooth surfaces, the fourth piston tooth 14 and the fourth stator tooth 32 have respectively inclined flat tooth surfaces,
wherein the annular piston 10 can be driven to axially reciprocate, wherein the first piston tooth 11 is engaged with the first stator tooth 21, then the second piston tooth 12 is engaged with the second stator tooth 22, the third piston tooth 13 is engaged with the third stator tooth 31, then the fourth piston tooth 14 is engaged with the fourth stator tooth 32, thereby pushing the annular piston 10 to rotate.
The annular piston 10, the first stator 20, and the second stator 30 may be formed in a substantially tubular shape, respectively, and coaxially disposed. The rotation of the annular piston 10 is about its central axis.
Referring to fig. 5, when the annular piston 10 is meshed with the first stator 20, the first piston tooth 11 is meshed with the first stator tooth 21, that is, the initial meshing of the annular piston 10 and the first stator 20 is realized by the tooth meshing of the curved tooth surface, that is, the curved tooth surface is of a conventional tooth structure, and the design can lead to less abrasion between teeth, stable transmission, labor saving, low durable noise and the like, and of course, even if the axial relative movement of the two is uniform, the circumferential relative movement caused by meshing is non-uniform; then, the second piston tooth 12 meshes with the second stator tooth 22, and the two teeth are shaped structures of different conventional teeth, i.e. tooth surfaces are planes, and an included angle is formed between the planes and the axial direction (or the center line of the teeth), so that when the axial relative movement is uniform, the circumferential movement of the annular piston 10 relative to the first stator 20 is also uniform, i.e. uniform rotation is realized.
In the stage where the first piston tooth 11 is engaged with the first stator tooth 21, the second piston tooth 12 is not engaged with the second stator tooth 22, and when the second piston tooth 12 starts to engage with the second stator tooth 22, the first piston tooth 11 starts to disengage from the first stator tooth 21.
The manner of engagement of the third piston teeth 13, the fourth piston teeth 14 and the second stator 30 of the annular piston 10 is substantially the same as the manner of engagement of the annular piston 10 and the first stator described above, and will not be repeated here.
Alternatively, the first piston tooth 11, the first stator tooth 21, the third piston tooth 13 and the third stator tooth 31 each have involute tooth surfaces. That is, the curved tooth surface is an involute tooth surface, that is, a tooth surface structure of teeth in a conventional gear.
Wherein the first piston tooth 11 and the second piston tooth 12 are located radially inward and outward, respectively, and the third piston tooth 13 and the fourth piston tooth 14 are located radially inward and outward, respectively. As shown in fig. 1 to 4, the annular piston 10 is provided with teeth at both axial ends, and the teeth at each end are provided with inner and outer layers, respectively, and correspondingly, the two stators engaged with the annular piston 10 are also provided with teeth of inner and outer layers, respectively. It should be noted that, the tooth portion of the curved tooth surface or the tooth portion of the flat tooth surface may be provided in the outer layer or the inner layer.
Wherein, the first piston tooth 11 and the second piston tooth 12 are in one-to-one correspondence and the center line is aligned, the first stator tooth 21 and the second stator tooth 22 are in one-to-one correspondence and the center line is aligned, the third piston tooth 13 and the fourth piston tooth 14 are in one-to-one correspondence and the center line is aligned, and the third stator tooth 31 and the fourth stator tooth 32 are in one-to-one correspondence and the center line is aligned. The teeth on the annular piston 10, the first stator 20 and the second stator 30 can be in an axisymmetric structure, and the teeth on the radial outer layer and the teeth on the radial inner layer have the same tooth number and are aligned in the center line, so that the structure is more convenient to process and manufacture. Of course, in other embodiments, the outer and inner teeth of the annular piston 10, the first stator 20, the second stator 30 may be staggered, so long as tooth engagement by curved flanks is ensured followed by tooth engagement by flat flanks.
Wherein the center lines of the first stator tooth portion 21 and the second stator tooth portion 22 are offset from the center lines of the third stator tooth portion 31 and the fourth stator tooth portion 32, and the center lines of the first piston tooth portion 11 and the second piston tooth portion 12 are aligned with the center lines of the third piston tooth portion 13 and the fourth piston tooth portion 14. In this structure, when the annular piston 10 is fully engaged with the first stator 20, the center line of the first piston tooth 11 is aligned with the tooth root of the first stator tooth 21, and the center line of the third piston tooth 13 is offset from the tooth root of the third stator tooth 31, so that when the annular piston 10 is disengaged from the first stator 20 and engaged with the second stator 30, the third piston tooth 13 and the third stator tooth 31 are necessarily caused to move relatively in the circumferential direction, that is, the center line of the third piston tooth 13 is prevented from being aligned with the tooth root of the third stator tooth 31, and when the annular piston 10 and the second stator 30 are prevented from being engaged with each other, no relative movement in the circumferential direction is generated between the annular piston 10 and the second stator 30. The design is such that the annular piston 10 can rotate continuously as it reciprocates axially.
In other embodiments, the center lines of the first and second piston teeth 11 and 12 may be offset from the center lines of the third and fourth piston teeth 13 and 14, and it is necessary to correspondingly adjust the relative positional relationship of the center lines of the first and second stator teeth 21 and 22 with the center lines of the third and fourth stator teeth 31 and 32, thereby ensuring that when the tooth portion of one end of the annular piston 10 is aligned with the tooth root of the corresponding stator, the tooth portion of the other end is offset from the tooth root of the corresponding stator.
Alternatively, the distance between the tooth tips of the first and second piston teeth 11 and 12 and the tooth tips of the third and fourth piston teeth 13 and 14 is greater than the distance between the tooth tips of the first and second stator teeth 21 and 22 and the tooth tips of the third and fourth stator teeth 31 and 32, and is less than the distance between the tooth tips of the first and second stator teeth 21 and 22 and the tooth tips of the third and fourth stator teeth 31 and 32. The distance between the tips of the teeth at both ends of the annular piston 10 is smaller than the distance between the tips of the teeth of the two stators, which allows the teeth at one end of the annular piston 10 to be disengaged from the teeth of the corresponding stator, while the teeth at the other end of the annular piston 10 are already in engagement with the teeth of the corresponding stator, i.e. the teeth at least one end of the annular piston 10 remain in engagement with the teeth of the corresponding stator, which allows the annular piston 10 to remain in circumferential movement, such that there is always circumferential movement, i.e. rotational continuity, when the annular piston 10 is axially moved. In addition, the distance between the tooth tips at both ends of the annular piston 10 is smaller than the distance between the tooth tip of any one stator and the tooth root of the other stator, i.e., when the annular piston 10 is fully engaged with one of the stators (the tooth tip of the piston tooth is engaged with the tooth root of the stator tooth), the piston tooth at the other end thereof is disengaged from the tooth tip of the other stator tooth, so that the annular piston 10 can be allowed to rotate circumferentially to pass over the tooth tip of the other stator.
As shown in fig. 5, the engagement process of the first and second piston teeth 11 and 12 with the first and second stator teeth 21 and 22 is shown, and at the beginning stage, the first piston teeth 11 and 21 each having a curved tooth surface start to be engaged, but the second piston teeth 12 and 22 are disengaged from each other and not engaged, and at step 3 of fig. 5, the second piston teeth 12 and 22 start to be engaged, and at the same time the first piston teeth 11 and 21 start to be disengaged.
It should be noted that, for a curved tooth surface, the contour line thereof is a smooth curve, and in the direction from the tooth tip to the tooth root, the angle between the tangent line of the contour line and the central axis of the tooth gradually decreases, and the tangent line at each point on the contour line corresponds to the relative movement direction of the tooth at the time of meshing at that point; similarly, for a flat surface tooth surface, the contour is a straight line, and the angle between the straight line and the center line of the tooth remains constant. When the first piston tooth 11 and the first stator tooth 21 start to disengage and the second piston tooth 12 and the second stator tooth 22 start to engage, the tangential direction of the tooth surface at the engagement point of the first piston tooth 11 and the first stator tooth 21 is the same as the tangential direction of the tooth surface of the first piston tooth 11 and the first stator tooth 21 (actually, the direction of the tooth surface contour line), and smooth transition is achieved. The fitting structure of the third piston tooth 13 and the fourth piston tooth 14 with the third stator tooth 31 and the fourth stator tooth 32 at the other end of the annular piston 10 is also the same, and will not be described in detail here.
The rotary driving mechanism comprises two groups of first stators 20, second stators 30 and annular pistons 10 which are axially arranged, wherein the first stators 20 and the second stators 30 of the two groups are relatively fixed, and the two annular pistons 10 are circumferentially relatively fixed and can axially relatively move. As shown in fig. 1 and 2, two sets of the first stator 20, the second stator 30 and the annular piston 10 are arranged in the axial direction, and in particular, one set of the second stator 30 and the other set of the first stator 20 are connected to each other, and may be integrally formed. The functions of the two groups of structures are basically the same, the overall reliability can be improved, and when one group is damaged, the other group can be used.
In particular, the centre lines of the first piston teeth 11 of the two annular pistons 10 are offset. When the rotary drive mechanism is shut down, it is optional to move one of the annular pistons 10 into full engagement with one of the stators, achieving self-locking, i.e. when external torque is applied to the annular piston 10, the annular piston 10 will not be caused to rotate. That is, if the piston teeth on one end of the first annular piston 10 are fully engaged with the stator teeth while the rotary drive mechanism is processing the non-actuated state, the annular piston 10 is axially moved at this time, and the piston teeth on the other end are engaged with the stator teeth in such a manner that the annular piston 10 can be rotated only in one direction; meanwhile, the second annular piston 10 is in an incomplete meshing state, the annular piston 10 is driven to move in opposite axial directions, the rotation directions of the annular piston 10 are just opposite, namely, the rotation directions can be determined by selecting the axial movement directions of the annular piston 10, and the second annular piston 10 can drive the first annular piston 10 to rotate, so that the axial movement of the two annular pistons is realized.
Referring to fig. 6 and 7, the tooth portions are shown in a planar expanded view, wherein the serial numbers represent the sequence of steps. When the initial positions of the two annular pistons 10 (hereinafter, the left annular piston 10 and the right annular piston 10 are distinguished from each other) are the same, the left annular piston 10 is at the self-locking position, and both end teeth of the right annular piston 10 are engaged with the corresponding stator tooth portions. In fig. 6, the left annular piston 10 and the right annular piston 10 are driven to move rightward at the same time, the right annular piston 10 is guided by the second stator 30 to rotate upwards, so that the left annular piston 10 can be driven to rotate upwards, and then the two annular pistons 10 are driven to reciprocate axially, so that continuous upwards rotation is realized; in fig. 7, the right annular piston 10 is driven to move axially leftwards, and the left annular piston 10 is driven to move axially rightwards, the right annular piston 10 rotates downwards under the guidance of the first stator 20, so that the left annular piston 10 can be driven to rotate downwards, and then the two annular pistons 10 are driven to reciprocate axially continuously, so that continuous downwards rotation is realized.
In addition, the rotary drive mechanism includes an inner ring 40, two of the annular pistons 10 are axially slidably mounted to the inner ring 40, and the two annular pistons 10 are circumferentially fixed with respect to the inner ring 40. The annular piston 10 may be mounted to the inner ring 40 by a spline-in-spline fit, and thus may move axially relative to the inner ring 40, but may not rotate circumferentially relative thereto. The inner ring 40 is limited in the direction of movement by a relatively fixed structure, i.e. it can only rotate relative to the respective stator and cannot move axially relative to the stator, for example, a structure for guiding the inner ring 40 may be provided on a plurality of stators. As shown in fig. 2, the inner ring 40 passes through the stator and the annular piston, and an end cap 50 may be provided at the other end thereof, and the end cap 50 may restrict axial movement of the inner ring 40 and achieve sealing. The end cap 50 may be annular in shape and the integral rotary drive mechanism is provided with a central bore to allow passage of the pipeline therethrough.
A cavity for accommodating movement of the two annular pistons 10 may be provided in a structure in which the first stator 20 and the second stator 30 are integrally connected, and the annular pistons 10 may be driven to move axially by supplying hydraulic power to the cavity.
In addition, the invention also provides a cantilever crane, wherein the cantilever crane is provided with the rotary driving mechanism. The stator part may be fixed relative to one arm section of the arm support and the annular piston 10, in particular the inner ring 40, may cooperate with another adjacent arm section to rotate the other arm section.
In addition, the invention also provides engineering machinery, wherein the engineering machinery is provided with the arm support. The engineering machinery can be a concrete pump truck, a crane and the like.
The preferred embodiments of the present invention have been described in detail above with reference to the accompanying drawings, but the present invention is not limited thereto. Within the scope of the technical idea of the invention, a number of simple variants of the technical solution of the invention are possible, including combinations of individual specific technical features in any suitable way. The various possible combinations of the invention are not described in detail in order to avoid unnecessary repetition. Such simple variations and combinations are likewise to be regarded as being within the scope of the present disclosure.
Claims (13)
1. A rotary drive mechanism characterized in that the rotary drive mechanism comprises an annular piston (10) and a stator, the annular piston (10) is provided with a piston tooth having a protruding curved tooth surface and a piston tooth having an inclined flat tooth surface, the stator is provided with a stator tooth having a protruding curved tooth surface and a stator tooth having an inclined flat tooth surface, the annular piston (10) is drivable to move axially relative to the stator, and the annular piston (10) is engaged with the stator tooth having a protruding curved tooth surface by the piston tooth having a protruding curved tooth surface and then with the stator tooth having an inclined flat tooth surface by the piston tooth having an inclined flat tooth surface to drive the annular piston (10) to rotate circumferentially.
2. The rotary drive mechanism according to claim 1, wherein the stator comprises a first stator (20) and a second stator (30) in the shape of a ring, the annular piston (10) being arranged between the first stator (20) and the second stator (30).
3. The rotary drive mechanism according to claim 2, characterized in that the annular piston (10) is provided with a first piston tooth (11) and a second piston tooth (12) at its axial first end and with a third piston tooth (13) and a fourth piston tooth (14) at its axial second end, the first stator (20) being provided with a first stator tooth (21) capable of meshing with the first piston tooth (11) and a second stator tooth (22) capable of meshing with the second piston tooth (12), the second stator (30) being provided with a third stator tooth (31) capable of meshing with the third piston tooth (13) and a fourth stator tooth (32) capable of meshing with the fourth piston tooth (14), the first piston tooth (11) and the first stator tooth (21) having respectively protruding curved tooth surfaces, the second piston tooth (12) and the second stator tooth (22) having respectively inclined tooth surfaces, the third stator tooth (31) and the fourth stator tooth (32) having respectively inclined tooth surfaces,
wherein the annular piston (10) can be driven to axially reciprocate, wherein the first piston tooth (11) is meshed with the first stator tooth (21) first, then the second piston tooth (12) is meshed with the second stator tooth (22), the third piston tooth (13) is meshed with the third stator tooth (31) first, then the fourth piston tooth (14) is meshed with the fourth stator tooth (32) so as to push the annular piston (10) to rotate.
4. A rotary drive mechanism according to claim 3, characterized in that the first piston tooth (11), the first stator tooth (21), the third piston tooth (13) and the third stator tooth (31) each have involute tooth surfaces.
5. A rotary drive mechanism according to claim 3, characterized in that the first piston teeth (11) and the second piston teeth (12) are located radially inside and outside, respectively, and the third piston teeth (13) and the fourth piston teeth (14) are located radially inside and outside, respectively.
6. The rotary drive mechanism according to claim 5, wherein the first piston teeth (11) and the second piston teeth (12) are in one-to-one correspondence and centerline alignment, the first stator teeth (21) and the second stator teeth (22) are in one-to-one correspondence and centerline alignment, the third piston teeth (13) and the fourth piston teeth (14) are in one-to-one correspondence and centerline alignment, and the third stator teeth (31) and the fourth stator teeth (32) are in one-to-one correspondence and centerline alignment.
7. The rotary drive mechanism according to claim 6, characterized in that the centerlines of the first and second stator teeth (21, 22) are offset from the centerlines of the third and fourth stator teeth (31, 32), and the centerlines of the first and second piston teeth (11, 12) are aligned with the centerlines of the third and fourth piston teeth (13, 14).
8. The rotary drive mechanism according to claim 7, characterized in that the distance between the tooth tips of the first piston tooth (11) and the second piston tooth (12) and the tooth tips of the third piston tooth (13) and the fourth piston tooth (14) is greater than the distance between the tooth tips of the first stator tooth (21) and the second stator tooth (22) and the tooth tips of the third stator tooth (31) and the fourth stator tooth (32), and is smaller than the distance between the tooth tips of the first stator tooth (21) and the second stator tooth (22) and the tooth tips of the third stator tooth (31) and the fourth stator tooth tip (32).
9. The rotary drive mechanism according to claim 8, characterized in that it comprises two sets of the first stator (20), the second stator (30) and the annular piston (10) arranged axially, the first stator (20) and the second stator (30) of the two sets being relatively fixed, the two annular pistons (10) being relatively fixed circumferentially and axially movable.
10. Rotary drive mechanism according to claim 9, characterized in that the centre lines of the first piston teeth (11) of the two annular pistons (10) are offset.
11. The rotary drive mechanism according to claim 9, characterized in that it comprises an inner ring (40), that both annular pistons (10) are axially slidably mounted to the inner ring (40), and that both annular pistons (10) are circumferentially fixed with respect to the inner ring (40).
12. A boom, characterized in that the boom is provided with a rotary drive mechanism according to any one of claims 1-11.
13. A construction machine, characterized in that the construction machine is provided with a boom according to claim 12.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210259497.3A CN116792358A (en) | 2022-03-16 | 2022-03-16 | Rotary driving mechanism, arm support and engineering machinery |
| PCT/CN2022/135571 WO2023173810A1 (en) | 2022-03-16 | 2022-11-30 | Rotary driving mechanism, boom, and engineering machinery |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210259497.3A CN116792358A (en) | 2022-03-16 | 2022-03-16 | Rotary driving mechanism, arm support and engineering machinery |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116792358A true CN116792358A (en) | 2023-09-22 |
Family
ID=88022133
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210259497.3A Pending CN116792358A (en) | 2022-03-16 | 2022-03-16 | Rotary driving mechanism, arm support and engineering machinery |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN116792358A (en) |
| WO (1) | WO2023173810A1 (en) |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2399586A1 (en) * | 1977-08-02 | 1979-03-02 | Anvar | STEP MOTOR AND / OR BRAKE DEVICE |
| US4771646A (en) * | 1987-01-05 | 1988-09-20 | Vetco Gray Inc. | Rotating and indexing mechanism |
| JP2628452B2 (en) * | 1993-12-29 | 1997-07-09 | 株式会社スリーデイコンポリサーチ | Stepping actuator |
| JPH08303410A (en) * | 1995-04-27 | 1996-11-19 | Hino Motors Ltd | Fluid pressure cylinder |
| FR2907869B1 (en) * | 2006-10-31 | 2009-11-27 | Robotiques 3 Dimensions Sarl | ACTUATING DEVICE TRANSFORMING A MOVEMENT OF VA AND COMING TO TRANSLATION OR ROTATION MOVEMENT |
| FR2910076B1 (en) * | 2006-12-19 | 2009-03-06 | Alfa Laval Moatti Soc Par Acti | HYDRAULIC MOTOR |
| AT511833B1 (en) * | 2011-11-10 | 2013-03-15 | Schwing Gmbh F | MASTER CONSTRUCTION, ESPECIALLY FOR A AUTOBETON PUMP |
| AT520549B1 (en) * | 2017-12-22 | 2019-05-15 | Schwing Gmbh F | Hydraulic rotary drive |
| CN213231293U (en) * | 2020-09-23 | 2021-05-18 | 中联重科股份有限公司 | Rotary driving mechanism, arm support assembly and engineering machinery |
-
2022
- 2022-03-16 CN CN202210259497.3A patent/CN116792358A/en active Pending
- 2022-11-30 WO PCT/CN2022/135571 patent/WO2023173810A1/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| WO2023173810A1 (en) | 2023-09-21 |
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