CN220396422U - Resonance-free vibration gearbox - Google Patents

Abstract

The utility model belongs to the technical field of engineering machinery, and discloses a resonance-free vibration gearbox, which comprises a box body, a gear phase converter, an eccentric gear set, a transition gear, a first driving assembly and a second driving assembly, wherein the first driving assembly and the second driving assembly are respectively arranged at two ends of the box body; through scientific structural design, add gear phase place converter in vibrating gear box, when starting and shut down, two sets of paired gear eccentric blocks, adjust the relative position between each gear eccentric block through gear phase place converter, make the vertical and horizontal exciting force that gear eccentric block produced offset each other. The utility model can adjust eccentric moment in the starting or stopping process, and eliminate resonance phenomenon of the vibration gearbox in the starting or stopping process.

Description

Resonance-free vibration gearbox

Technical Field

The utility model relates to the technical field of engineering machinery, in particular to a resonance-free vibration gearbox.

Background

The hydraulic vibration hammer is one of important equipment in pile foundation construction, and can generate exciting force through high-speed rotation of eccentric blocks in a vibration gear box, so that soil around a pile body can be liquefied, pile soil resistance is reduced, and the aim of pile sinking is achieved rapidly.

The vibration gearbox generates vertical exciting force by means of rotation of the paired eccentric mass blocks, resonance phenomenon of equipment can occur during starting and stopping, and excessive vibration can be caused to adjacent buildings particularly in urban areas, so that the use of the vibration hammer in urban areas is limited.

The prior art, the document with the application number of CN201710259597.5 discloses a hydraulic vibration hammer, which comprises a vibration damper, a vibration damper and a clamping device, wherein the vibration damper comprises a vibration excitation box, a top plate, a vibration damping frame, vibration damping rubber, a vibration damping cover, a safety mechanism, a secondary vibration damping frame and vibration damping rubber, wherein the top plate is in linkage with the vibration excitation box, the vibration damping frame is arranged on the top plate, the vibration damping rubber is uniformly distributed on the vibration damping frame, the vibration damping cover is connected with the vibration damping frame, the safety mechanism is arranged between the vibration damping frame and the vibration damping cover, the secondary vibration damping frame and the vibration damping rubber is arranged on the secondary vibration damping frame, an eccentric wheel with a semicircular cross section, a gear and a main shaft are arranged in the vibration excitation box, the gear and the eccentric wheel are correspondingly provided with mounting holes for mounting the main shaft, a motor connector is arranged between the top plate and the vibration excitation box, the eccentric wheel and the gear are integrally forged and formed, a bearing is sleeved between the bearing and the main shaft, and the main shaft are in linkage connection; the roof be the mounting panel, the mounting panel is equipped with the lower roof that is connected and parallel laminating with the mounting panel can be dismantled for the other end department of being connected one end with the shock absorber frame.

The vibration excitation box of the vibration hammer is provided with paired eccentric wheels, the vibration excitation box is rotated by virtue of the paired eccentric wheels to generate vertical exciting forces, centrifugal forces in the horizontal directions generated by the paired eccentric wheels are mutually offset, and the centrifugal forces in the vertical directions are mutually overlapped to generate mutually overlapped vertical exciting forces, the eccentric moment of the eccentric wheels of the vibration excitation box is not adjustable, the vibration excitation box can generate resonance phenomenon of equipment when being started and stopped, serious influence is caused on the equipment, the fault rate is increased, the service life is reduced, and meanwhile, the large amplitude and noise generated by resonance also cause adverse influence on the health of staff and the surrounding environment.

Therefore, there is a need to develop a resonance-free vibration gearbox, which can adjust the eccentric moment during the starting or stopping process, eliminate the resonance phenomenon of the vibration gearbox during the starting or stopping process, reduce the equipment failure rate, and prolong the equipment life.

Disclosure of Invention

The utility model aims to overcome the defects, and provides a resonance-free vibration gearbox, which is characterized in that a gear phase converter is additionally arranged in the vibration gearbox through a scientific structural design, and the relative positions of two pairs of gear eccentric blocks are regulated through the gear phase converter when the gear eccentric blocks are started and stopped, so that the vertical and horizontal exciting forces generated by the gear eccentric blocks are mutually offset.

The technical scheme is as follows:

the resonance-free vibration gearbox comprises a box body, a gear phase converter, an eccentric gear set, a transition gear, a first driving assembly and a second driving assembly, wherein the first driving assembly and the second driving assembly are respectively arranged at two ends of the box body, the eccentric gear set is arranged in the middle of the box body, the transition gear is arranged between the first driving assembly and the eccentric gear set, and the gear phase converter is arranged between the second driving assembly and the eccentric gear set; the gear phase converter comprises a first phase conversion gear and a second phase conversion gear, the eccentric gear set comprises a first eccentric gear, a second eccentric gear, a third eccentric gear and a fourth eccentric gear, the first driving assembly and the second driving assembly are respectively provided with a first driving gear and a second driving gear, the first driving gear, the transition gear, the first eccentric gear, the second eccentric gear and the first phase conversion gear are sequentially connected in a meshed mode, and the second driving gear, the second phase conversion gear, the third eccentric gear and the fourth eccentric gear are sequentially connected in a meshed mode.

The eccentric gear set comprises two pairs of gear eccentric blocks, the two pairs of gear eccentric blocks are four gear eccentric blocks, each gear eccentric block comprises an eccentric block and a gear, the eccentric blocks are connected with the gear in an integrated manner, and the gears of the four gear eccentric blocks are respectively a first eccentric gear, a second eccentric gear, a third eccentric gear and a fourth eccentric gear.

The gear phase converter further comprises a phase conversion main shaft, a first gear shaft sleeve, a second gear shaft sleeve, a first gear bearing, a second gear bearing, a first bearing seat, a second bearing seat, a first single-acting hydraulic cylinder, a second single-acting hydraulic cylinder and two phase conversion pin sleeve assemblies, wherein the phase conversion main shaft is hollow and cylindrical, the phase conversion main shaft comprises a left half section and a right half section, the left half section of the phase conversion main shaft is provided with a right-handed first spiral strip-shaped hole and a second spiral strip-shaped hole, the right half section of the phase conversion main shaft is provided with a left-handed third spiral strip-shaped hole and a fourth spiral strip-shaped hole, and the spiral phase angles of the first spiral strip-shaped hole, the second spiral strip-shaped hole, the third spiral strip-shaped hole and the fourth spiral strip-shaped hole are respectively 90 degrees and are sequentially staggered by 90 degrees; the side wall of the first gear shaft sleeve is provided with a first phase change pin hole and a second phase change pin hole which are opposite to each other, and the side wall of the second gear shaft sleeve is provided with a third phase change pin hole and a fourth phase change pin hole which are opposite to each other; the outer ring of the first gear shaft sleeve is provided with the first gear bearing and a first phase change gear, and the first gear bearing and the first phase change gear are arranged in the first bearing seat through the first gear bearing; the outer ring of the second gear shaft sleeve is provided with the second gear bearing and a second phase change gear, and is arranged in the second bearing seat through the second gear bearing; the left end of the phase transformation main shaft penetrates through the inner ring of the first gear shaft sleeve to be matched with a first pushing shaft of a first single-acting hydraulic cylinder, and one phase transformation pin sleeve component sequentially penetrates through a first phase transformation pin hole, a first spiral strip-shaped hole, a second spiral strip-shaped hole and a second phase transformation pin hole; the right end of the phase transformation main shaft penetrates through the inner ring of the second gear shaft sleeve to be matched with a second pushing shaft of the second single-acting hydraulic oil cylinder, and the other phase transformation pin sleeve component sequentially penetrates through a third phase transformation pin hole, a third spiral strip-shaped hole, a fourth spiral strip-shaped hole and a fourth phase transformation pin hole.

The gear shaft sleeve is characterized by further comprising a first lock nut, a second lock nut, a third lock nut, a fourth lock nut, a first limiting plate and a second limiting plate, wherein the first limiting plate separates the outer side face of the first gear shaft sleeve to form a first bearing installation section and a first gear installation shaft section, the first phase change gear is installed on the first gear installation shaft section through the first lock nut, and the first gear bearing is installed on the first bearing installation section through the second lock nut; the second limiting plate separates the outer side face of the second gear shaft sleeve to form a second bearing installation section and a second gear installation shaft section, the second phase change gear is installed on the second gear installation shaft section through the third locking nut, and the second gear bearing is installed on the second bearing installation section through the fourth locking nut.

The first phase change gear and the first limiting plate are respectively provided with a plurality of first pin holes and second pin holes matched with the first pin holes, and the first pin holes are respectively pinned into the first pin holes and the second pin holes; and the second phase change gear and the second limiting plate are respectively provided with a plurality of third pin holes and fourth pin holes matched with the second pins, and the second pins are pinned into the third pin holes and the fourth pin holes.

The phase change main shaft comprises a first gear shaft sleeve, a second gear shaft sleeve, a first single-action hydraulic cylinder and a second single-action hydraulic cylinder, wherein the inner side wall of the first gear shaft sleeve is provided with a first abrasion-resistant groove; the second wear-resisting groove is formed in the inner side wall of the second gear shaft sleeve, the second wear-resisting sleeve is installed in the second wear-resisting groove, and the right end of the phase change main shaft penetrates through the second wear-resisting sleeve of the inner ring of the second gear shaft sleeve to be matched with a second pushing shaft of the second single-acting hydraulic oil cylinder.

The first single-acting hydraulic cylinder comprises a first cylinder body, a first piston and a first support bearing, the first pushing shaft is arranged in the first piston through the first support bearing and is arranged in the first cylinder body through the first piston, and the first cylinder body is fixed on the first bearing seat through a screw; the second single-acting hydraulic cylinder comprises a second cylinder body, a second piston and a second support bearing, the second pushing shaft is installed in the second piston through the second support bearing and is installed in the second cylinder body through the second piston, and the second cylinder body is fixed on the second bearing seat through a screw.

The phase conversion main shaft comprises a phase conversion main shaft, and is characterized by further comprising a first rotary butt joint shaft and a second rotary butt joint shaft, wherein the first rotary butt joint shaft and the second rotary butt joint shaft are respectively arranged at the left end and the right end of the phase conversion main shaft, two first rotary keys are arranged on the end face of the first rotary butt joint shaft, two second rotary keys are arranged on the end face of the second rotary butt joint shaft, two third rotary keys are arranged on the end face of the first push shaft, two fourth rotary keys are arranged on the end face of the second push shaft, and the left end of the phase conversion main shaft is matched with the two third rotary keys of the first push shaft through the two first rotary keys of the first rotary butt joint shaft; the right end of the phase conversion main shaft is matched with two fourth rotary keys of the second pushing shaft through two second rotary keys of the second rotary butt joint shaft.

The oil cylinder is characterized by further comprising a first sealing ring, a first wear-resistant ring, a second sealing ring and a second wear-resistant ring, wherein a first sealing groove and a second sealing groove are formed in the outer side face of the first piston; the second piston is provided with a third sealing groove and a fourth sealing groove on the outer side face, the second sealing ring and the second wear-resistant ring are respectively arranged on the third sealing groove and the fourth sealing groove, and the second piston is sealed with the inner side wall of the second cylinder body through the second sealing ring and the second wear-resistant ring.

The phase change pin sleeve assembly comprises a pin shaft, a first guiding wear-resistant sleeve, a second guiding wear-resistant sleeve, a middle supporting sleeve, a third guiding wear-resistant sleeve and a fourth guiding wear-resistant sleeve, wherein the first guiding wear-resistant sleeve, the second guiding wear-resistant sleeve, the middle supporting sleeve, the third guiding wear-resistant sleeve and the fourth guiding wear-resistant sleeve are sequentially sleeved on the outer surface of the pin shaft and are respectively in rotary sliding connection with the pin shaft.

It should be noted that:

the foregoing "first and second …" do not represent a specific number or order, but are merely for distinguishing between names.

In the description of the present utility model, it should be understood that the azimuth or positional relationship indicated by the terms "left", "right", etc. are based on the azimuth or positional relationship shown in fig. 5, or the azimuth or positional relationship conventionally put in use of the product of the present utility model, or the azimuth or positional relationship conventionally understood by those skilled in the art, are merely for convenience of describing the present utility model and simplifying the description, and do not indicate or imply that the apparatus or element to be referred to must have a specific azimuth, be constructed and operated in a specific azimuth, and thus should not be construed as limiting the present utility model.

The direction indicated by the aforementioned "inner" means the direction toward the rotational central axis of the present gear phase converter.

The direction indicated by the outer refers to the direction away from the rotation central axis of the present gear phase converter.

The advantages and principles of the utility model are described below:

1. the utility model provides a resonance-free vibration gearbox, which comprises a box body, a gear phase converter, an eccentric gear set, a transition gear, a first driving assembly and a second driving assembly, wherein the eccentric gear set comprises a first eccentric gear, a second eccentric gear, a third eccentric gear and a fourth eccentric gear; that is, if the vibration gearbox provided with the gear phase converter is started or stopped, when the gear phase converter is driven to axially move to a full stroke, the vertical and horizontal exciting forces generated by the eccentric mass blocks of the eccentric gear set in the vibration gearbox are mutually counteracted, and the resonance phenomenon of the vibration gearbox in the starting or stopping process is eliminated; the resonance-free vibration gearbox can adjust the relative position among the gear eccentric blocks through the gear phase converter, and can adjust eccentric moment in the starting or stopping process, so that vertical and horizontal exciting forces generated by the gear eccentric blocks are mutually offset, resonance phenomenon of the vibration gearbox in the starting or stopping process is eliminated, equipment failure rate is reduced, equipment service life is prolonged, and adverse effects on health of operators and surrounding environment are reduced.

2. The eccentric gear set comprises two pairs of gear eccentric blocks, the eccentric blocks of the gear eccentric blocks are integrally connected with the gears, and the problem of loosening of screws of the split gear eccentric blocks can be avoided in the use process of the integrated gear eccentric blocks, so that the use reliability and the service life of the vibration gear box are improved.

3. The gear phase converter also comprises a phase conversion main shaft, a first gear shaft sleeve, a second gear shaft sleeve, a first gear bearing, a second gear bearing, a first bearing seat, a second bearing seat, a first single-acting hydraulic cylinder, a second single-acting hydraulic cylinder and two phase conversion pin sleeve components, wherein the first phase conversion gear and the first gear shaft sleeve form a whole and are connected with a right-hand first spiral strip-shaped hole and a second spiral strip-shaped hole of the phase conversion main shaft through the phase conversion pin sleeve components, and when the first phase conversion gear rotates, the phase conversion main shaft is driven to rotate through the phase conversion pin sleeve components; similarly, as the second phase change gear and the second gear shaft sleeve form a whole and are connected with the left-hand third spiral strip-shaped hole and the fourth spiral strip-shaped hole of the phase change main shaft through the phase change pin sleeve assembly, the phase change main shaft is driven to rotate through the phase change pin sleeve assembly when the second phase change gear rotates; when the phase change device is used, the first single-acting hydraulic oil cylinder pushes the first push shaft to move right and axially, the phase change main shaft is pushed to move right and axially by the first push shaft, meanwhile, the first phase change gear rotates clockwise along the first spiral strip-shaped hole and the second spiral strip-shaped hole by the phase change pin sleeve assembly, and when the first push shaft moves right to a full stroke, the first phase change gear rotates clockwise by 90 degrees; the second phase change gear rotates anticlockwise along the third spiral strip-shaped hole and the fourth spiral strip-shaped hole through the phase change pin sleeve assembly, and when the first pushing shaft moves rightwards to reach full stroke, the second phase change gear rotates anticlockwise by 90 degrees; through transmission chain analysis, the first phase change gear rotates clockwise, so that the first driving gear rotates clockwise in the same direction as the original rotation direction, and the second phase change gear rotates anticlockwise, so that the second phase change gear can be used as a fixed reference because the motor cannot rotate reversely in the normal rotation process, and the first phase change gear rotates clockwise by 180 degrees relative to the second phase change gear, namely the first driving gear rotates clockwise in a speed increasing manner. Because the vibration gearbox generates vertical exciting force by means of rotation of the paired eccentric wheels, centrifugal forces in the horizontal direction generated by the paired eccentric wheels are mutually offset, centrifugal forces in the vertical direction are mutually overlapped, so that mutually overlapped vertical exciting forces are generated, for example, two second eccentric gears and a third eccentric gear which are mutually overlapped in the vertical direction are respectively meshed with a first phase conversion gear and a second phase conversion gear, when the first thrust direction moves right to a full stroke, the first phase conversion gear rotates 180 degrees clockwise relative to the second phase conversion gear, namely the second eccentric gear meshed with the first phase conversion gear rotates 180 degrees anticlockwise relative to the third eccentric gear meshed with the second phase conversion gear, namely centrifugal force of the second eccentric gear and centrifugal force of the third eccentric gear are mutually offset, and the first eccentric gear meshed with the second eccentric gear rotates 180 degrees clockwise relative to a fourth eccentric gear meshed with the third eccentric gear, namely centrifugal force of the first eccentric gear and centrifugal force of the fourth eccentric gear are mutually offset, so that eccentric moment adjustment is realized; that is, if the vibration gearbox provided with the gear phase converter is started or stopped, when the first pushing shaft of the first single-acting hydraulic oil cylinder is pushed to move right to the full stroke, the vertical exciting force and the horizontal exciting force generated by the eccentric mass block of the eccentric wheel in the vibration gearbox are mutually counteracted, and the resonance phenomenon of the vibration gearbox in the starting or stopping process is eliminated.

Similarly, the second single-acting hydraulic cylinder pushes the second push shaft to move left and right, and pushes the phase conversion main shaft to move left and right through the second push shaft, and meanwhile, the second phase conversion gear rotates clockwise along the third spiral strip-shaped hole and the fourth spiral strip-shaped hole through the phase conversion pin sleeve assembly, and when the second push shaft moves right to reach full stroke, the second phase conversion gear rotates clockwise by 90 degrees; the first phase change gear rotates anticlockwise along the first spiral strip-shaped hole and the second spiral strip-shaped hole through the phase change pin sleeve assembly, and when the second pushing shaft moves leftwards to reach full stroke, the first phase change gear rotates anticlockwise by 90 degrees; through transmission chain analysis, the second phase change gear rotates clockwise, so that the second driving gear rotates anticlockwise, the same as the original rotation direction, and the first phase change gear rotates anticlockwise, so that the first driving gear rotates anticlockwise, and the opposite to the original rotation direction, because the motor cannot rotate reversely in the normal rotation process, the first phase change gear can be used as a fixed reference, and then the second phase change gear rotates 180 degrees clockwise relative to the first phase change gear, namely the second driving gear rotates anticlockwise at a speed increasing speed. When the first pushing shaft moves leftwards to the full stroke, the third eccentric gear meshed with the second phase change gear rotates 180 degrees anticlockwise relative to the second eccentric gear meshed with the first phase change gear, so that the eccentric moment is readjusted; when the rotating speed of the eccentric mass block of the eccentric wheel in the vibration gear box reaches a stable working frequency, the second pushing shaft of the second single-acting hydraulic oil cylinder is pushed to move leftwards to reach a full stroke, the eccentric mass block of the eccentric wheel in the vibration gear box generates horizontal exciting forces which are mutually offset and vertical exciting forces are mutually overlapped, the generated vibration is maximum (maximum amplitude), when the eccentric mass block of the eccentric wheel in the vibration gear box reaches the maximum frequency, the relative position (0 degree < adjustment angle <180 degrees) of the eccentric mass block is started to be adjusted, so that the eccentric mass block generates vibration (0 degree < amplitude < maximum amplitude), and the pile is driven to vibrate and sink into a foundation. The relative position between the gear eccentric blocks can be adjusted through the gear phase converter in the vibration gear box, so that the eccentric moment of the gear eccentric blocks is adjusted, the vertical and horizontal exciting forces generated by the gear eccentric blocks during starting or stopping in the vibration gear box are mutually offset, and the resonance phenomenon and the influence on the surrounding environment of the vibration gear box during starting or stopping are eliminated; when the amplitude of the vibration gearbox is required to be adjusted, the relative position of the eccentric mass block in the vibration gearbox can be adjusted by adjusting the stroke of the single-acting hydraulic cylinder in the gear phase converter, so that the required amplitude is generated, and the adjustment of the vertical exciting force of the vibration gearbox is realized.

4. The utility model also comprises a first lock nut, a second lock nut, a third lock nut and a fourth lock nut, wherein external connecting threads are respectively arranged at the left end of a first bearing installation section and the right end of a first gear installation shaft section of the first gear shaft sleeve, and the first gear bearing and the first phase change gear are respectively installed on the first gear shaft sleeve through the second lock nut and the first lock nut, so that the installation stability of the first gear bearing and the first phase change gear is improved. And similarly, the third lock nut and the fourth lock nut are used for improving the installation stability of the second gear bearing and the second phase change gear.

5. The utility model also comprises a first limiting plate, a second limiting plate, a first pin and a second pin, wherein the first phase change gear and the second phase change gear are respectively pinned on the first limiting plate and the second limiting plate through the first pin and the second pin, so that the limiting stability of the first phase change gear and the second phase change gear is improved.

6. The utility model also comprises a first wear-resistant sleeve and a second wear-resistant sleeve, wherein the first wear-resistant sleeve and the second wear-resistant sleeve are arranged for improving the wear resistance of the inner walls of the first gear shaft sleeve and the second gear shaft sleeve and the phase change main shaft.

7. The first single-acting hydraulic cylinder comprises a first cylinder body, a first piston and a first support bearing, wherein the first push shaft is arranged in the first piston through the first support bearing, so that the first push shaft rotates in the first piston more smoothly, and the second single-acting hydraulic cylinder comprises a second cylinder body, a second piston and a second support bearing, and the second push shaft is arranged in the second piston through the second support bearing, so that the second push shaft rotates in the second piston more smoothly.

8. The utility model also comprises a first rotary butt joint shaft and a second rotary butt joint shaft, and rotary keys are respectively arranged on the end surfaces of the rotary butt joint shaft and the pushing shaft, so that the pushing of the pushing shaft is more stable by utilizing the cooperation of the rotary keys.

9. The utility model further comprises a first sealing ring, a first wear-resistant ring, a second sealing ring and a second wear-resistant ring, and the sealing performance of the piston and the cylinder body of the oil cylinder is improved by arranging the sealing ring and the wear-resistant ring on the outer side surface of the piston.

10. The phase change pin sleeve assembly comprises a pin shaft, a first guide wear-resistant sleeve, a second guide wear-resistant sleeve, a middle support sleeve, a third guide wear-resistant sleeve and a fourth guide wear-resistant sleeve, when the phase change pin sleeve assembly is used, the four guide wear-resistant sleeves respectively prop against a spiral strip-shaped hole and a phase change pin hole, the wear resistance of the phase change pin sleeve assembly is improved, a lubricating oil groove is further arranged between the middle support sleeve and the guide wear-resistant sleeve when the phase change pin sleeve assembly is designed, and gear oil can enter between each guide wear-resistant sleeve and the pin shaft from the lubricating oil groove to lubricate, so that the guide wear-resistant sleeve and the pin shaft rotate more smoothly.

Drawings

Fig. 1 is a schematic perspective view of a resonance-free vibration gearbox according to an embodiment of the utility model.

FIG. 2 is a schematic perspective sectional view of a resonance-free vibration gearbox according to an embodiment of the present utility model.

Fig. 3 is a schematic perspective view of the vibration gearbox housing hidden by the resonance-free vibration gearbox according to the embodiment of the utility model.

Fig. 4 is a schematic perspective view of a gear phase converter according to an embodiment of the present utility model.

Fig. 5 is a schematic perspective sectional structure of a gear phase changer according to an embodiment of the present utility model.

Fig. 6 is an exploded view of a gear phase converter according to an embodiment of the present utility model.

Fig. 7 is a schematic perspective view of a phase change spindle according to an embodiment of the present utility model.

Fig. 8 is a schematic top view of a phase change spindle according to an embodiment of the present utility model.

Fig. 9 is a schematic view of the cross-sectional A-A configuration of fig. 8.

Fig. 10 is a schematic view of the cross-sectional B-B structure of fig. 8.

Fig. 11 is a schematic bottom view of a phase change spindle according to an embodiment of the present utility model.

Fig. 12 is a schematic perspective view of a first gear sleeve according to an embodiment of the present utility model.

Fig. 13 is a schematic perspective sectional view of a first gear sleeve according to an embodiment of the present utility model.

Fig. 14 is a schematic perspective view of a second gear sleeve according to an embodiment of the present utility model.

Fig. 15 is a schematic perspective sectional view of a second gear sleeve according to an embodiment of the present utility model.

Fig. 16 is a schematic perspective view of a first phase change gear according to an embodiment of the present utility model.

Fig. 17 is a schematic perspective view of a second phase change gear according to an embodiment of the present utility model.

Fig. 18 is a schematic perspective view of a first rotary docking shaft according to an embodiment of the present utility model.

Fig. 19 is a schematic perspective view of a second rotary docking shaft according to an embodiment of the present utility model.

Fig. 20 is a schematic perspective view of a first pushing shaft according to an embodiment of the present utility model.

Fig. 21 is a schematic perspective view of a second pushing shaft according to an embodiment of the present utility model.

Fig. 22 is a schematic perspective sectional view of a phase change pin sleeve assembly according to an embodiment of the present utility model.

Fig. 23 is a schematic structural view of an eccentric mass of an eccentric in accordance with an embodiment of the present utility model in a non-resonant condition.

FIG. 24 is a schematic view of an eccentric mass adjustable eccentric moment condition of an eccentric in accordance with an embodiment of the present utility model.

Fig. 25 is a schematic structural view of the eccentric mass maximum eccentric moment state of the eccentric wheel according to the embodiment of the present utility model.

Fig. 26 is a schematic diagram of the structure of the gear eccentric block changing the motion state when the first thrust shaft moves right to the full stroke according to the embodiment of the present utility model.

Fig. 27 is a schematic diagram of a structure of the gear eccentric block in the case that the second thrust shaft moves leftwards to the full stroke in the embodiment of the present utility model.

Reference numerals illustrate:

10. a gear phase changer 11, a phase change main shaft 111, a first spiral bar hole 112, a second spiral bar hole 113, a third spiral bar hole 114, a fourth spiral bar hole 12, a first rotary docking shaft 121, a first rotary key 13, a second rotary docking shaft 131, a second rotary key 20, a first gear sleeve 21, a first phase change pin hole 22, a second phase change pin hole 23, a first lock nut 24, a second lock nut 25, a first limiting plate 251, a second pin hole 26, a first bearing mounting section 261, a first wear groove 27, a first gear mounting shaft section 28, a first pin 29, a first wear sleeve 30, a second gear sleeve 31, a third phase change pin hole 32, a fourth phase change pin hole 33, a third lock nut 34, a fourth lock nut 35, a second limiting plate, 351, fourth pin holes, 36, second bearing mounting section, 361, second wear grooves, 37, second gear mounting shaft section, 38, second pin, 39, second wear sleeve, 41, first gear bearing, 42, second gear bearing, 43, first bearing housing, 44, second bearing housing, 45, first phase change gear, 451, first pin holes, 46, second phase change gear, 461, third pin holes, 50, first single-acting hydraulic cylinder, 51, first push shaft, 511, third rotary key, 52, first cylinder, 53, first piston, 531, first seal ring, 532, first wear ring, 54, first support bearing, 60, second single-acting hydraulic cylinder, 61, second push shaft, 611, fourth rotary key, 62, second cylinder, 63, second piston, 631, second seal ring, 632, second wear ring, 64, second support bearing, 70. the phase change pin bush assembly, 71, a pin shaft, 72, a first guiding wear-resistant bush, 73, a second guiding wear-resistant bush, 74, an intermediate supporting bush, 75, a third guiding wear-resistant bush, 76, a fourth guiding wear-resistant bush, 81, a box, 82, an eccentric gear set, 821, a first eccentric gear, 822, a second eccentric gear, 823, a third eccentric gear, 824, a fourth eccentric gear, 83, a transition gear, 84, a first driving assembly, 841, a first driving gear, 85, a second driving assembly, 851 and a second driving gear.

Detailed Description

The following describes embodiments of the present utility model in detail.

The resonance-free vibration gear box provided by the embodiment of the utility model is particularly applied to equipment such as ASV400 hydraulic vibration hammers produced by China, and the hydraulic pile hammer equipment using the resonance-free vibration gear box can adjust eccentric moment in the starting or stopping process of the vibration gear box, eliminate resonance phenomenon of the vibration gear box in the starting or stopping process, prolong the service life of the equipment, and avoid adverse effects of large amplitude and noise of resonance on the health of operators and the surrounding environment.

In order that the utility model may be readily understood, a more complete description of the utility model will be rendered by reference to the appended drawings. Preferred embodiments of the present utility model are shown in the drawings. This utility model may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this utility model belongs. The terminology used herein in the description of the utility model is for the purpose of describing particular embodiments only and is not intended to be limiting of the utility model.

Reference will now be made in detail to exemplary embodiments, examples of which are illustrated in the accompanying drawings. When the following description refers to the accompanying drawings, the same numbers in different drawings refer to the same or similar elements, unless otherwise indicated. The implementations described in the following exemplary examples are not representative of all implementations consistent with the present disclosure. Rather, they are merely examples of apparatus and methods consistent with some aspects of the present disclosure as detailed in the accompanying claims.

Examples

Referring to fig. 1 to 27, the resonance-free vibration gearbox provided in this embodiment includes a box 81, a gear phase converter 10, an eccentric gear set 82, a transition gear 83, a first drive assembly 84, and a second drive assembly 85, wherein the first drive assembly 84 and the second drive assembly 85 are respectively installed at two ends of the box 81, the eccentric gear set 82 is installed in the middle of the box 81, the transition gear 83 is installed between the first drive assembly 84 and the eccentric gear set 82, and the gear phase converter 10 is installed between the second drive assembly 85 and the eccentric gear set 82; the gear phase converter 10 includes a first phase conversion gear 45 and a second phase conversion gear 46, the eccentric gear train 82 includes a first eccentric gear 821, a second eccentric gear 822, a third eccentric gear 823, and a fourth eccentric gear 824, the first drive assembly 84 and the second drive assembly 85 include a first drive gear 841 and a second drive gear 851, respectively, the first drive gear 841, the transition gear 83, the first eccentric gear 821, the second eccentric gear 822, and the first phase conversion gear 45 are sequentially engaged with each other, and the second drive gear 851, the second phase conversion gear 46, the third eccentric gear 823, and the fourth eccentric gear 824 are sequentially engaged with each other.

The resonance-free vibration gearbox is characterized in that a gear phase converter 10 is additionally arranged in the vibration gearbox through scientific structural design and cooperative cooperation of all parts, and a phase conversion main shaft 11 of the gear phase converter 10 is driven to axially move, so that a first phase conversion gear 45 rotates 180 degrees clockwise relative to a second phase conversion gear 46, namely a second eccentric gear 822 meshed with the first phase conversion gear 45 rotates 180 degrees anticlockwise relative to a third eccentric gear 823 meshed with the second phase conversion gear 46, namely centrifugal force of the second eccentric gear 822 and centrifugal force of the third eccentric gear 823 are counteracted, and a first eccentric gear 821 meshed with the second eccentric gear 822 rotates 180 degrees clockwise relative to a fourth eccentric gear 824 meshed with the third eccentric gear 823, namely centrifugal force of the first eccentric gear 821 and centrifugal force of the fourth eccentric gear 824 are counteracted, so that eccentric moment adjustment is realized; that is, if the vibration gearbox provided with the present gear phase converter 10 is started or stopped, when the gear phase converter 10 is driven to axially move to a full stroke, the vertical and horizontal exciting forces generated by the eccentric mass blocks of the eccentric gear set 82 in the vibration gearbox cancel each other out, eliminating the resonance phenomenon of the vibration gearbox during the starting or stopping process; the resonance-free vibration gearbox can adjust the relative position among the gear eccentric blocks through the gear phase converter 10, can adjust eccentric moment in the starting or stopping process, so that vertical and horizontal exciting forces generated by the gear eccentric blocks are mutually offset, the resonance phenomenon of the vibration gearbox in the starting or stopping process is eliminated, the equipment failure rate can be reduced, the equipment service life is prolonged, the adverse influence of noise during operation on the health of operators and on the surrounding environment is reduced, and the smooth construction is guaranteed.

The gear phase converter 10 further includes a phase conversion main shaft 11, a first gear shaft sleeve 20, a second gear shaft sleeve 30, a first gear bearing 41, a second gear bearing 42, a first bearing seat 43, a second bearing seat 44, a first single-acting hydraulic cylinder 50, a second single-acting hydraulic cylinder 60, and two phase conversion pin sleeve assemblies 70, the phase conversion main shaft 11 is a hollow cylindrical type, the phase conversion main shaft 11 includes a left half section and a right half section, a right-handed first spiral strip-shaped hole 111 and a second spiral strip-shaped hole 112 are provided on the left half section of the phase conversion main shaft 11, a left-handed third spiral strip-shaped hole 113 and a fourth spiral strip-shaped hole 114 are provided on the right half section of the phase conversion main shaft 11, and the spiral phase angles of the first spiral strip-shaped hole 111, the second spiral strip-shaped hole 112, the third spiral strip-shaped hole 113 and the fourth spiral strip-shaped hole 114 are respectively 90 ° and are sequentially staggered by 90 °. The side wall of the first gear shaft sleeve 20 is provided with a first phase change pin hole 21 and a second phase change pin hole 22 which are opposite to each other, and the side wall of the second gear shaft sleeve 30 is provided with a third phase change pin hole 31 and a fourth phase change pin hole 32 which are opposite to each other; a first gear bearing 41 and a first phase change gear 45 are mounted on the outer ring of the first gear sleeve 20, and are mounted in a first bearing seat 43 through the first gear bearing 41; a second gear bearing 42 and a second phase change gear 46 are mounted on the outer ring of the second gear sleeve 30, and are mounted in a second bearing seat 44 through the second gear bearing 42; the left end of the phase conversion main shaft 11 passes through the inner ring of the first gear shaft sleeve 20 to be matched with the first push shaft 51 of the first single-acting hydraulic oil cylinder 50, and one phase conversion pin sleeve assembly 70 sequentially passes through the first phase conversion pin hole 21, the first spiral strip hole 111, the second spiral strip hole 112 and the second phase conversion pin hole 22; the right end of the phase conversion main shaft 11 passes through the inner ring of the second gear shaft sleeve 30 to be matched with the second pushing shaft 61 of the second single-acting hydraulic oil cylinder 60, and the other phase conversion pin sleeve assembly 70 sequentially passes through the third phase conversion pin hole 31, the third spiral strip hole 113, the fourth spiral strip hole 114 and the fourth phase conversion pin hole 32.

Because the first phase change gear 45 and the first gear shaft sleeve 20 form a whole and are connected with the right-handed first spiral strip-shaped hole 111 and the second spiral strip-shaped hole 112 of the phase change main shaft 11 through the phase change pin sleeve assembly 70, the phase change main shaft 11 is driven to rotate through the phase change pin sleeve assembly 70 when the first phase change gear 45 rotates; similarly, since the second phase change gear 46 and the second gear sleeve 30 form a whole and are connected with the left-handed third spiral strip-shaped hole 113 and the fourth spiral strip-shaped hole 114 of the phase change main shaft 11 through the phase change pin sleeve assembly 70, the phase change main shaft 11 is driven to rotate through the phase change pin sleeve assembly 70 when the second phase change gear 46 rotates; in use, the first single-acting hydraulic cylinder 50 pushes the first push shaft 51 to move rightward and axially, and pushes the phase conversion main shaft 11 to move rightward and axially through the first push shaft 51, and simultaneously the first phase conversion gear 45 rotates clockwise along the first spiral bar-shaped hole 111 and the second spiral bar-shaped hole 112 through the phase conversion pin sleeve assembly 70, and when the first push shaft 51 moves rightward to reach full stroke, the first phase conversion gear 45 rotates clockwise by 90 degrees; the second phase change gear 46 will rotate counterclockwise along the third helical strip hole 113 and the fourth helical strip hole 114 through the phase change pin sleeve assembly 70, and when the first push shaft 51 moves rightward to the full stroke, the second phase change gear 46 will rotate counterclockwise by 90 °; referring to fig. 26, by analyzing the driving chain, the first phase change gear 45 rotates clockwise, which causes the first driving gear 841 to rotate clockwise in the same direction as the original rotation direction, and the second phase change gear 46 rotates counterclockwise, which causes the second driving gear 851 to rotate clockwise, which is opposite to the original rotation direction, because the motor cannot rotate reversely during the normal rotation, and thus the second phase change gear 46 can be used as a fixed reference, the first phase change gear 45 rotates clockwise by 180 ° with respect to the second phase change gear 46, i.e., the first driving gear 841 rotates at a clockwise speed. Because the vibration gearbox generates vertical exciting force by means of rotation of the paired eccentric wheels, centrifugal forces in the horizontal direction generated by the paired eccentric wheels are mutually offset, centrifugal forces in the vertical direction are mutually overlapped, so that mutually overlapped vertical exciting forces are generated, for example, two second eccentric gears 822 and third eccentric gears 823 with centrifugal forces mutually overlapped in the vertical direction are respectively meshed with the first phase conversion gear 45 and the second phase conversion gear 46, when the first push shaft 51 moves rightwards to reach full stroke, the first phase conversion gear 45 rotates 180 degrees clockwise relative to the second phase conversion gear 46, namely, the second eccentric gear 822 meshed with the first phase conversion gear 45 rotates 180 degrees anticlockwise relative to the third eccentric gear 823 meshed with the second phase conversion gear 46, namely, centrifugal force of the second eccentric gear 822 and centrifugal force of the third eccentric gear 823 are mutually offset, and the first eccentric gear 821 meshed with the second eccentric gear 822 rotates 180 degrees clockwise relative to the fourth eccentric gear 824 meshed with the third eccentric gear 823, namely, centrifugal force of the first eccentric gear 821 and centrifugal force of the fourth gear 824 are mutually offset, and therefore adjustment of the moment is achieved; that is, if the vibration gearbox provided with the present gear phase converter 10 is started or stopped, when the first push shaft 51 of the first single-acting hydraulic cylinder 50 is pushed to move rightward to the full stroke, as shown in fig. 23, the vertical and horizontal exciting forces generated by the eccentric mass of the eccentric wheel in the vibration gearbox cancel each other, eliminating the resonance phenomenon of the vibration gearbox during the starting or stopping.

Similarly, the second single-acting hydraulic cylinder 60 pushes the second push shaft 61 to move axially leftwards, and pushes the phase change main shaft 11 to move axially leftwards through the second push shaft 61, and at the same time, the second phase change gear 46 rotates clockwise along the third spiral strip-shaped hole 113 and the fourth spiral strip-shaped hole 114 through the phase change pin sleeve assembly 70, and when the second push shaft 61 moves rightwards to the full stroke, the second phase change gear 46 rotates clockwise by 90 degrees; the first phase change gear 45 will rotate counterclockwise along the first helical strip hole 111 and the second helical strip hole 112 by the phase change pin sleeve assembly 70, and when the second push shaft 61 moves to the left to the full stroke, the first phase change gear 45 will rotate counterclockwise by 90 °; referring to fig. 27, by analyzing the driving chain, the second phase change gear 46 rotates clockwise, which causes the second driving gear 851 to rotate counterclockwise in the same direction as the original rotation, and the first phase change gear 45 rotates counterclockwise, which causes the first driving gear 841 to rotate counterclockwise in the opposite direction to the original rotation, and thus the first phase change gear 45 can be used as a fixed reference because the motor cannot rotate reversely during the normal rotation, and then the second phase change gear 46 rotates clockwise by 180 ° with respect to the first phase change gear 45, i.e., the second driving gear 851 rotates counterclockwise at a speed increasing. When the first push shaft 51 moves leftwards to the full stroke, the third eccentric gear 823 meshed with the second phase conversion gear 46 rotates 180 degrees anticlockwise relative to the second eccentric gear 822 meshed with the first phase conversion gear 45, so that the eccentric moment is readjusted; when the rotation speed of the eccentric mass block of the eccentric wheel in the vibration gearbox reaches a stable working frequency, the second pushing shaft 61 of the second single-acting hydraulic oil cylinder 60 is pushed to move leftwards to reach a full stroke, as shown in fig. 25, the horizontal exciting forces generated by the eccentric mass block of the eccentric wheel in the vibration gearbox are mutually offset, the vertical exciting forces are mutually overlapped, the generated vibration is maximum (maximum amplitude), and when the eccentric mass block of the eccentric wheel in the vibration gearbox reaches the maximum frequency, as shown in fig. 24, the relative position (0 ° < adjustment angle <180 °) of the eccentric mass block is started to generate vibration (0 < amplitude < maximum amplitude), so that the pile is driven to sink into the foundation in a vibration mode. The relative position between the gear eccentric blocks can be adjusted through the gear phase converter 10 in the vibration gear box, so that the eccentric moment of the gear eccentric blocks is adjusted, the vertical and horizontal exciting forces generated by the gear eccentric blocks during starting or stopping in the vibration gear box are mutually offset, and the resonance phenomenon and the influence on the surrounding environment of the vibration gear box during starting or stopping are eliminated; when the amplitude of the vibration gearbox is required to be adjusted, the relative position of the eccentric mass block in the vibration gearbox can be adjusted by adjusting the stroke of the single-acting hydraulic cylinder in the gear phase converter 10, so that the required amplitude is generated, and the adjustment of the vertical exciting force of the vibration gearbox is realized.

The eccentric gear set 82 includes two pairs of gear eccentric blocks, the two pairs of gear eccentric blocks are four gear eccentric blocks, the gear eccentric blocks include eccentric blocks and gears, the eccentric blocks are connected with the gears in an integrated manner, and the gears of the four gear eccentric blocks are a first eccentric gear 821, a second eccentric gear 822, a third eccentric gear 823 and a fourth eccentric gear 824 respectively. The problem that the screws of the split gear eccentric blocks are loosened in the use process of the integrated gear eccentric blocks is solved, and the use reliability and the service life of the vibration gearbox are improved.

The phase change pin sleeve assembly 70 comprises a pin shaft 71, a first guiding wear-resistant sleeve 72, a second guiding wear-resistant sleeve 73, a middle supporting sleeve 74, a third guiding wear-resistant sleeve 75 and a fourth guiding wear-resistant sleeve 76, wherein the first guiding wear-resistant sleeve 72, the second guiding wear-resistant sleeve 73, the middle supporting sleeve 74, the third guiding wear-resistant sleeve 75 and the fourth guiding wear-resistant sleeve 76 are sequentially sleeved on the outer surface of the pin shaft 71 and are respectively in rotary sliding connection with the pin shaft 71. When the guide wear-resistant sleeve is used, the four guide wear-resistant sleeves are respectively abutted against the spiral strip-shaped holes and the phase change pin holes, so that the wear resistance of the phase change pin sleeve assembly 70 is improved, and in design, a lubricating oil groove is further formed between the middle support sleeve 74 and the guide wear-resistant sleeve, and gear oil can enter between each guide wear-resistant sleeve and the pin shaft 71 from the lubricating oil groove to lubricate, so that the guide wear-resistant sleeve and the pin shaft 71 rotate more smoothly.

The first single-acting hydraulic cylinder 50 comprises a first cylinder body 52, a first piston 53 and a first support bearing 54, the first push shaft 51 is arranged in the first piston 53 through the first support bearing 54 and is arranged in the first cylinder body 52 through the first piston 53, and the first cylinder body 52 is fixed on the first bearing seat 43 through screws; the second single-acting hydraulic cylinder 60 includes a second cylinder body 62, a second piston 63, and a second support bearing 64, the second push shaft 61 is mounted in the second piston 63 through the second support bearing 64, and is mounted in the second cylinder body 62 through the second piston 63, and the second cylinder body 62 is fixed on the second bearing housing 44 through screws. The first push shaft 51 is mounted in the first piston 53 through the first support bearing 54, so that the first push shaft 51 rotates in the first piston 53 more smoothly, and similarly, the second push shaft 61 is mounted in the second piston 63 through the second support bearing 64, so that the second push shaft 61 rotates in the second piston 63 more smoothly.

The utility model further comprises a first lock nut 23, a second lock nut 24, a first limiting plate 25, a third lock nut 33, a fourth lock nut 34, a second limiting plate 35, a first wear-resistant sleeve 29, a second wear-resistant sleeve 39, a first rotary butt shaft 12, a second rotary butt shaft 13, a first sealing ring 531, a first wear-resistant ring 532, a second sealing ring 631, a second wear-resistant ring 632, a plurality of first pins 28 and a plurality of second pins 38, wherein the first limiting plate 25 separates the outer side surface of the first gear shaft sleeve 20 to form a first bearing mounting section 26 and a first gear mounting shaft section 27, the first phase change gear 45 is mounted on the first gear mounting shaft section 27 through the first lock nut 23, and the first gear bearing 41 is mounted on the first bearing mounting section 26 through the second lock nut 24; the second limiting plate 35 separates the outer side surface of the second gear sleeve 30 to form a second bearing mounting section 36 and a second gear mounting shaft section 37, the second phase change gear 46 is mounted on the second gear mounting shaft section 37 through the third lock nut 33, and the second gear bearing 42 is mounted on the second bearing mounting section 36 through the fourth lock nut 34. External connecting threads are respectively arranged at the left end of the first bearing mounting section 26 and the right end of the first gear mounting shaft section 27 of the first gear shaft sleeve 20, and the first gear bearing 41 and the first phase conversion gear 45 are respectively mounted on the first gear shaft sleeve 20 through the second locking nut 24 and the first locking nut 23, so that the mounting stability of the first gear bearing 41 and the first phase conversion gear 45 is improved. Similarly, the third lock nut 33 and the fourth lock nut 34 are provided to improve the stability of the installation of the second gear bearing 42 and the second phase change gear 46.

The first phase change gear 45 and the first limiting plate 25 are respectively provided with a plurality of first pin holes 451 and second pin holes 251 matched with the first pins 28, and the first pins 28 are respectively pinned into the first pin holes 451 and the second pin holes 251; the second phase change gear 46 and the second limiting plate 35 are respectively provided with a plurality of third pin holes 461 and fourth pin holes 351 matched with the second pin 38, and the second pin 38 is pinned into the third pin holes 461 and the fourth pin holes 351. The limit stability of the first phase change gear 45 and the second phase change gear 46 is improved.

The inner side wall of the first gear shaft sleeve 20 is provided with a first wear-resistant groove 261, a first wear-resistant sleeve 29 is arranged in the first wear-resistant groove 261, and the left end of the phase change main shaft 11 passes through the first wear-resistant sleeve 29 of the inner ring of the first gear shaft sleeve 20 to be matched with the first push shaft 51 of the first single-acting hydraulic oil cylinder 50; the second abrasion-resistant groove 361 is arranged on the inner side wall of the second gear shaft sleeve 30, the second abrasion-resistant sleeve 39 is arranged in the second abrasion-resistant groove 361, and the right end of the phase change main shaft 11 passes through the second abrasion-resistant sleeve 39 of the inner ring of the second gear shaft sleeve 30 and is matched with the second pushing shaft 61 of the second single-acting hydraulic oil cylinder 60. The first wear-resistant sleeve 29 and the second wear-resistant sleeve 39 are used for improving the wear resistance of the inner walls of the first gear sleeve 20 and the second gear sleeve 30 and the phase change main shaft 11.

The first rotary butt joint shaft 12 and the second rotary butt joint shaft 13 are respectively arranged at the left end and the right end of the phase conversion main shaft 11, two first rotary keys 121 are arranged on the end face of the first rotary butt joint shaft 12, two second rotary keys 131 are arranged on the end face of the second rotary butt joint shaft 13, two third rotary keys 511 are arranged on the end face of the first push shaft 51, two fourth rotary keys 611 are arranged on the end face of the second push shaft 61, and the left end of the phase conversion main shaft 11 is matched with the two third rotary keys 511 of the first push shaft 51 through the two first rotary keys 121 of the first rotary butt joint shaft 12; the right end of the phase conversion main shaft 11 is engaged with the two fourth rotation keys 611 of the second push shaft 61 through the two second rotation keys 131 of the second rotation butt shaft 13. The pushing of the pushing shaft is more stable by utilizing the cooperation of the rotary keys.

The outer side surface of the first piston 53 is provided with a first sealing groove and a second sealing groove, a first sealing ring 531 and a first wear-resistant ring 532 are respectively arranged on the first sealing groove and the second sealing groove, and the first piston 53 is sealed with the inner side wall of the first cylinder body 52 through the first sealing ring 531 and the first wear-resistant ring 532; the outer side surface of the second piston 63 is provided with a third sealing groove and a fourth sealing groove, the second sealing ring 631 and the second wear-resistant ring 632 are respectively arranged on the third sealing groove and the fourth sealing groove, and the second piston 63 is sealed with the inner side wall of the second cylinder body 62 through the second sealing ring 631 and the second wear-resistant ring 632. The sealing ring and the wear-resistant ring are arranged on the outer side surface of the piston, so that the tightness between the piston and the cylinder body of the oil cylinder is improved.

The ASV400 hydraulic vibrating hammer device disclosed by the utility model is produced and used by China, and has the advantages that prototype test application is carried out, and the result shows that the hydraulic vibrating hammer device disclosed by the utility model can be used for adjusting eccentric moment in the starting or stopping process of a vibrating gear box, eliminating resonance phenomenon of the vibrating gear box in the starting or stopping process, avoiding large amplitude and noise generated by resonance, prolonging the service life of the device and reducing adverse effects on operators and surrounding environments.

The foregoing is merely exemplary embodiments of the present utility model, and is not intended to limit the scope of the present utility model; any substitutions and modifications made without departing from the spirit of the utility model are within the scope of the utility model.

Claims (10)

1. The resonance-free vibration gearbox is characterized by comprising a box body, a gear phase converter, an eccentric gear set, a transition gear, a first driving assembly and a second driving assembly, wherein the first driving assembly and the second driving assembly are respectively arranged at two ends of the box body, the eccentric gear set is arranged in the middle of the box body, the transition gear is arranged between the first driving assembly and the eccentric gear set, and the gear phase converter is arranged between the second driving assembly and the eccentric gear set; the gear phase converter comprises a first phase conversion gear and a second phase conversion gear, the eccentric gear set comprises a first eccentric gear, a second eccentric gear, a third eccentric gear and a fourth eccentric gear, the first driving assembly and the second driving assembly are respectively provided with a first driving gear and a second driving gear, the first driving gear, the transition gear, the first eccentric gear, the second eccentric gear and the first phase conversion gear are sequentially connected in a meshed mode, and the second driving gear, the second phase conversion gear, the third eccentric gear and the fourth eccentric gear are sequentially connected in a meshed mode.

2. The resonance-free vibration gearbox of claim 1, wherein the eccentric gear set comprises two sets of paired gear eccentric blocks, the two sets of paired gear eccentric blocks are four gear eccentric blocks, the gear eccentric blocks comprise eccentric blocks and gears, the eccentric blocks are integrally connected with the gears, and the gears of the four gear eccentric blocks are respectively the first eccentric gear, the second eccentric gear, the third eccentric gear and the fourth eccentric gear.

3. The resonance-free vibration gearbox of claim 1, wherein the gear phase converter further comprises a phase conversion main shaft, a first gear shaft sleeve, a second gear shaft sleeve, a first gear bearing, a second gear bearing, a first bearing seat, a second bearing seat, a first single-acting hydraulic cylinder, a second single-acting hydraulic cylinder and two phase conversion pin sleeve assemblies, the phase conversion main shaft is hollow cylindrical, the phase conversion main shaft comprises a left half section and a right half section, a right-handed first spiral strip-shaped hole and a second spiral strip-shaped hole are arranged on the left half section of the phase conversion main shaft, a left-handed third spiral strip-shaped hole and a fourth spiral strip-shaped hole are arranged on the right half section of the phase conversion main shaft, and the spiral phase angles of the first spiral strip-shaped hole, the second spiral strip-shaped hole, the third spiral strip-shaped hole and the fourth spiral strip-shaped hole are respectively 90 degrees and are sequentially staggered by 90 degrees; the side wall of the first gear shaft sleeve is provided with a first phase change pin hole and a second phase change pin hole which are opposite to each other, and the side wall of the second gear shaft sleeve is provided with a third phase change pin hole and a fourth phase change pin hole which are opposite to each other; the outer ring of the first gear shaft sleeve is provided with the first gear bearing and a first phase change gear, and the first gear bearing and the first phase change gear are arranged in the first bearing seat through the first gear bearing; the outer ring of the second gear shaft sleeve is provided with the second gear bearing and a second phase change gear, and is arranged in the second bearing seat through the second gear bearing; the left end of the phase transformation main shaft penetrates through the inner ring of the first gear shaft sleeve to be matched with a first pushing shaft of a first single-acting hydraulic cylinder, and one phase transformation pin sleeve component sequentially penetrates through a first phase transformation pin hole, a first spiral strip-shaped hole, a second spiral strip-shaped hole and a second phase transformation pin hole; the right end of the phase transformation main shaft penetrates through the inner ring of the second gear shaft sleeve to be matched with a second pushing shaft of the second single-acting hydraulic oil cylinder, and the other phase transformation pin sleeve component sequentially penetrates through a third phase transformation pin hole, a third spiral strip-shaped hole, a fourth spiral strip-shaped hole and a fourth phase transformation pin hole.

4. A resonance-free vibration gearbox as claimed in claim 3, further comprising a first lock nut, a second lock nut, a third lock nut, a fourth lock nut, a first limiting plate, a second limiting plate, the first limiting plate separating the outer side of the first gear sleeve to form a first bearing mounting section, a first gear mounting shaft section, the first phase change gear being mounted to the first gear mounting shaft section by the first lock nut, the first gear bearing being mounted to the first bearing mounting section by the second lock nut; the second limiting plate separates the outer side face of the second gear shaft sleeve to form a second bearing installation section and a second gear installation shaft section, the second phase change gear is installed on the second gear installation shaft section through the third locking nut, and the second gear bearing is installed on the second bearing installation section through the fourth locking nut.

5. The resonance-free vibration gearbox of claim 4, further comprising a plurality of first pins and a plurality of second pins, wherein the first phase change gear and the first limiting plate are respectively provided with a plurality of first pin holes and second pin holes matched with the first pins, and the first pins are respectively pinned into the first pin holes and the second pin holes; and the second phase change gear and the second limiting plate are respectively provided with a plurality of third pin holes and fourth pin holes matched with the second pins, and the second pins are pinned into the third pin holes and the fourth pin holes.

6. The resonance-free vibration gearbox of claim 3, further comprising a first wear-resistant sleeve and a second wear-resistant sleeve, wherein a first wear-resistant groove is formed in the inner side wall of the first gear shaft sleeve, the first wear-resistant sleeve is arranged in the first wear-resistant groove, and the left end of the phase change main shaft penetrates through the first wear-resistant sleeve of the inner ring of the first gear shaft sleeve to be matched with the first pushing shaft of the first single-acting hydraulic cylinder; the second wear-resisting groove is formed in the inner side wall of the second gear shaft sleeve, the second wear-resisting sleeve is installed in the second wear-resisting groove, and the right end of the phase change main shaft penetrates through the second wear-resisting sleeve of the inner ring of the second gear shaft sleeve to be matched with a second pushing shaft of the second single-acting hydraulic oil cylinder.

7. The resonance-free vibration gearbox of any one of claims 3 to 6, wherein the first single-acting hydraulic ram comprises a first ram cylinder, a first piston, a first support bearing, the first push shaft being mounted in the first piston via the first support bearing and in the first ram cylinder via the first piston, the first ram cylinder being secured to the first bearing housing via a screw; the second single-acting hydraulic cylinder comprises a second cylinder body, a second piston and a second support bearing, the second pushing shaft is installed in the second piston through the second support bearing and is installed in the second cylinder body through the second piston, and the second cylinder body is fixed on the second bearing seat through a screw.

8. The resonance-free vibration gearbox of claim 7, further comprising a first rotary docking shaft and a second rotary docking shaft, wherein the first rotary docking shaft and the second rotary docking shaft are respectively arranged at the left end and the right end of the phase conversion main shaft, two first rotary keys are arranged on the end face of the first rotary docking shaft, two second rotary keys are arranged on the end face of the second rotary docking shaft, two third rotary keys are arranged on the end face of the first pushing shaft, two fourth rotary keys are arranged on the end face of the second pushing shaft, and the left end of the phase conversion main shaft is matched with the two third rotary keys of the first pushing shaft through the two first rotary keys of the first rotary docking shaft; the right end of the phase conversion main shaft is matched with two fourth rotary keys of the second pushing shaft through two second rotary keys of the second rotary butt joint shaft.

9. The resonance-free vibration gearbox of claim 8, further comprising a first sealing ring, a first wear ring, a second sealing ring and a second wear ring, wherein a first sealing groove and a second sealing groove are arranged on the outer side surface of the first piston, the first sealing ring and the first wear ring are respectively arranged on the first sealing groove and the second sealing groove, and the first piston is sealed with the inner side wall of the first cylinder body through the first sealing ring and the first wear ring; the second piston is provided with a third sealing groove and a fourth sealing groove on the outer side face, the second sealing ring and the second wear-resistant ring are respectively arranged on the third sealing groove and the fourth sealing groove, and the second piston is sealed with the inner side wall of the second cylinder body through the second sealing ring and the second wear-resistant ring.

10. The resonance-free vibration gearbox of claim 9, wherein the phase shift pin sleeve assembly comprises a pin shaft, a first guiding wear sleeve, a second guiding wear sleeve, a middle support sleeve, a third guiding wear sleeve, a fourth guiding wear sleeve, wherein the first guiding wear sleeve, the second guiding wear sleeve, the middle support sleeve, the third guiding wear sleeve, the fourth guiding wear sleeve are sequentially sleeved on the outer surface of the pin shaft and are respectively in rotary sliding connection with the pin shaft.