CN110439993B - Shock-resistant transmission - Google Patents
Shock-resistant transmission Download PDFInfo
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- CN110439993B CN110439993B CN201910738133.1A CN201910738133A CN110439993B CN 110439993 B CN110439993 B CN 110439993B CN 201910738133 A CN201910738133 A CN 201910738133A CN 110439993 B CN110439993 B CN 110439993B
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H61/0403—Synchronisation before shifting
- F16H2061/0414—Synchronisation before shifting by retarder control
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Gear Transmission (AREA)
- Retarders (AREA)
- Structure Of Transmissions (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention belongs to the technical field of transmissions, and particularly relates to an impact-resistant transmission which comprises a first shell, an input shaft, a connecting mechanism, an output shaft, a one-way clutch ring, a first shaft, a gear ring and the like, wherein the transmission is realized by using a simple structure; the invention utilizes the engagement of the driving bevel gear and other bevel gears to lead the gear to rotate, thus realizing the transmission of larger torque, and in addition, the gear revolves around the gear ring under the effect of gear shifting and speed increasing of the connecting structure, thus realizing the transmission of larger rotating speed under the double effects of rotation and revolution of the gear; the invention has simple structure and better use effect.
Description
Technical Field
The invention belongs to the technical field of transmissions, and particularly relates to an impact-resistant transmission.
Background
The traditional transmission generally performs speed change and gear shift according to gears in the transmission, and in the process of gear shift by using the gears in the transmission, a main driving gear needs to be meshed and gear shift among gears with different sizes, so that instant impact force can be generated in the process of instantly meshing the main driving gear and another gear, and the gear teeth of the transmission have certain impact damage.
The invention designs an anti-impact transmission to solve the problems.
Disclosure of Invention
In order to solve the defects in the prior art, the invention discloses an impact-resistant transmission which is realized by adopting the following technical scheme.
An impact resistant transmission characterized by: the device comprises a first shell, an input shaft, a connecting mechanism, an output shaft, a first ring sleeve, a one-way clutch ring, a first fixing plate, a ring disc, a second fixing plate, a third fixing plate, a fourth fixing plate, a first shaft, a second shaft, a third shaft, a gear ring, a disc, a cylindrical cavity, a mechanism hole, a shaft hole, a driving bevel gear, a first bevel gear, a second bevel gear, a third bevel gear, a fourth bevel gear, a fifth bevel gear and a sixth bevel gear, wherein the cylindrical cavity is formed in the first shell; one side surface of the first shell is provided with a mechanism hole, and the other side surface of the first shell is provided with a shaft hole; one end of the input shaft is provided with a driving bevel gear; the outer circular surface of the input shaft is provided with a connecting mechanism, and the connecting mechanism is positioned in the mechanism hole; the first ring sleeve is arranged on the outer circular surface of the input shaft and is positioned between the connecting mechanism and the driving bevel gear; the first ring sleeve is connected with the connecting mechanism; the ring disc is arranged at one end of the first ring sleeve and is positioned between the first ring sleeve and the driving bevel gear; a unidirectional clutch ring is arranged on the outer circular surface of the first ring sleeve; two first fixing plates are symmetrically arranged on the outer circular surface of the one-way clutch ring; one end of the first fixing plate, which is not connected with the one-way clutch ring, is connected with the inner cavity surface of the cylindrical cavity; two second fixing plates are symmetrically arranged on the disc surface of the annular disc close to the driving bevel gear; one ends of the two second fixing plates, which are not connected with the annular disc, are provided with third fixing plates; two fourth fixing plates are symmetrically arranged on the third fixing plate; the two first bevel gears are symmetrically arranged on the corresponding second fixing plates through axes; the two first bevel gears are respectively meshed with the driving bevel gears; a first shaft is arranged in the middle of the third fixing plate; one end of the first shaft is provided with a second bevel gear, and the other end of the first shaft is provided with a third bevel gear; the second bevel gear is positioned between the two second fixing plates and is respectively meshed with the two first bevel gears; a second shaft is arranged on each of the two fourth fixing plates; one end of the second shaft is provided with a fourth bevel gear, and the other end of the second shaft is provided with a fifth bevel gear; a third shaft is arranged at the two ends of the third fixing plate; one end of the third shaft is provided with a sixth bevel gear, and the other end of the third shaft is provided with a gear; the two fourth bevel gears are meshed with the third bevel gear; the two fifth bevel teeth are respectively meshed with the corresponding sixth bevel teeth.
The output shaft is arranged in the shaft hole; one end of the output shaft is provided with a disc which is positioned in the cylindrical cavity; the gear ring is arranged on the disc and positioned in the cylindrical cavity; the second fixing plate, the third fixing plate, the fourth fixing plate and the gear are all positioned in the gear ring; the gear is meshed with the gear ring.
The connecting mechanism comprises a second shell, a second ring sleeve, a volute spiral spring, a third ring sleeve, a fixing ring, a ring groove, a fourth ring sleeve, a first ring plate, a piston ring groove, a second ring plate, an inner key, an outer key, an inner key guide groove and an outer key guide groove, wherein the second shell is arranged in a mechanism hole; the second ring sleeve is arranged on the outer circular surface of the input shaft, and the outer circular surface of the second ring sleeve is in contact with the inner wall surface of the second shell; one side surface of the second ring sleeve is provided with a ring groove; the inner groove surface of the ring groove is provided with threads; the second ring plate is arranged on the side surface of the second ring sleeve with the ring groove; the third ring sleeve is arranged on the outer circular surface of the input shaft; a piston ring groove is formed in the side face of one end of the third ring sleeve, and the other end of the third ring sleeve is connected with the first ring sleeve; one end of the third ring sleeve, which is provided with the piston ring groove, is positioned in the second ring plate; two inner key guide grooves are symmetrically formed in the inner circular surface of the piston ring groove, and two outer key guide grooves are symmetrically formed in the outer circular surface of the piston ring groove; the fixing ring is nested on the outer circular surface of the third ring sleeve; the outer circular surface of the fixing ring is connected with the inner wall surface of the second shell; one end of the volute spiral spring is arranged on the inner circular surface of the second ring plate, and the other end of the volute spiral spring is arranged on the outer circular surface of the third ring sleeve; the fourth ring sleeve is arranged on the outer circular surface of the input shaft, and the outer circular surface of the fourth ring sleeve is provided with threads; the fourth ring sleeve is positioned in the ring groove of the second ring sleeve, and the threads on the fourth ring sleeve are matched with the threads on the inner groove surface of the ring groove of the second ring sleeve; one end of the first ring plate is arranged on the side surface of the fourth ring sleeve, and the other end of the first ring plate is provided with a piston ring; two inner keys are symmetrically arranged on the inner circular surface of the piston ring, and two outer keys are symmetrically arranged on the outer circular surface; the piston ring is positioned in the piston ring groove; the two inner keys are respectively positioned in the corresponding inner key guide grooves, and the two outer keys are respectively positioned in the corresponding outer key guide grooves; the piston ring slides in the piston ring groove by means of an inner key and an outer key.
As a further improvement of the present technology, the distance between the two ends of the third fixing plate and the corresponding second fixing plate is equal.
As a further improvement of the present technique, the maximum diameter of the sixth conical tooth is smaller than the diameter of the gear.
As a further improvement in the present technique, the distance from the axis of the drive bevel gear to the inner circumference of the ring gear is 4 times the distance from the axis of the gear to the inner circumference of the ring gear.
As a further improvement of the technology, one end of the input shaft, which is not provided with the driving bevel gear, is connected with a power device.
As a further improvement of the technology, one end of the output shaft, which is not connected with the disk, is connected with the actuating mechanism.
As a further improvement of the technology, high-pressure gas is filled between the piston ring and the piston ring groove.
As a further improvement of the present technique, the distance between the piston ring and the bottom surface of the third ring is maximized when the second ring is not rotated.
According to the invention, the first ring sleeve is provided with the one-way clutch ring, and the two first fixing plates are symmetrically arranged on the one-way clutch ring, so that the first ring sleeve is fixed and can rotate in the one-way clutch ring; the function of the unidirectional clutch ring is as follows: in the driving direction, the first ring sleeve can only rotate along a single direction, and the rotating direction is always the same as the rotating direction of the input shaft.
The ring disc is arranged on the first ring sleeve, the two second fixing plates are symmetrically arranged on the ring disc, the third fixing plate is arranged on the second fixing plate, the first ring sleeve can drive the second fixing plate to rotate around the axis of the first ring sleeve through the ring disc, and the second fixing plate drives the third fixing plate to rotate around the axis of the first ring sleeve.
The driving bevel gear is meshed with the first bevel gear, the first bevel gear is meshed with the second bevel gear, and the third bevel gear and the second bevel gear are both arranged on the first shaft, so that the driving bevel gear can drive the third bevel gear to rotate through the first bevel gear, the second bevel gear and the first shaft, and the rotating direction of the third bevel gear is opposite to that of the driving bevel gear; the third bevel gear is meshed with the fourth bevel gear, the fourth bevel gear and the fifth bevel gear are both arranged on the second shaft, the fifth bevel gear is meshed with the sixth bevel gear, the sixth bevel gear and the gear are both arranged on the third shaft, so that the third bevel gear can drive the gear to rotate through the fourth bevel gear, the second shaft, the fifth bevel gear, the sixth bevel gear and the third shaft, and the rotating direction of the third bevel gear is opposite to that of the gear; when the final driving bevel gear is transmitted to the gear through each bevel gear and the shaft, the rotating direction of the driving bevel gear is the same as that of the gear.
The gear is meshed with the gear ring, and the gear can drive the output shaft to rotate through the gear ring and the disc.
The distance from the axis of the driving bevel gear to the inner circle surface of the gear ring is 4 times of the distance from the axis of the gear to the inner circle surface of the gear ring, and the design is favorable for transmitting a larger transmission ratio.
In the above-described connection mechanism, the second housing is mounted in the mechanism hole, and then the second housing is fixed; the second ring sleeve is arranged on the input shaft, so that the input shaft can drive the second ring sleeve to rotate; the third ring sleeve is arranged on the outer circular surface of the input shaft, and the outer circular surface of the third ring sleeve is nested with the fixed ring, so that the third ring sleeve is fixed by the fixed ring and can rotate in the fixed ring; the third ring is connected with the first ring, so that the third ring can drive the first ring to rotate. The inner circle surface of the ring groove in the second ring sleeve is provided with threads, the outer circle surface of the fourth ring sleeve is provided with threads, the threads on the inner circle surface of the ring groove and the threads on the outer circle surface of the fourth ring sleeve are arranged in the ring groove in a thread matching mode, and then the fourth ring sleeve can axially move in the direction away from the ring groove under the condition that the fourth ring sleeve is not rotated by the rotation of the second ring sleeve; one end of the first ring plate is arranged on the fourth ring sleeve, and the other end of the first ring plate is provided with a piston ring, so that the fourth ring sleeve can drive the piston ring to axially move towards the inner side of the piston ring groove through the first ring plate; the piston ring is provided with an inner key and an outer key, the inner key slides in the inner key guide groove, the outer key slides in the outer key guide groove, and the fourth ring sleeve and the third ring sleeve are synchronous in the rotating direction due to the matching of the keys and the key grooves; as the ring compresses into the ring groove, the high pressure gas within the ring groove is compressed. The scroll spring is used for restoring the second ring sleeve and the fourth ring sleeve.
When the input shaft is not rotating, the distance between the piston ring and the piston ring groove is the largest, and the scroll spring is in the uncompressed state.
When the input shaft rotates to work, in the initial stage, the input shaft drives the driving bevel gear to rotate, the driving gear drives the gear to rotate through the first bevel gear, the second bevel gear, the third bevel gear, the fourth bevel gear, the fifth bevel gear and the sixth bevel gear, and when the gear rotates, a gear ring can provide reverse torque T1 for the gear according to the interaction of forces, and the reverse torque T1 is transmitted to a third fixing plate through a third shaft, so that the third fixing plate has a movement trend opposite to the rotation direction of the input shaft; meanwhile, the input shaft is matched with the thread of the fourth ring sleeve through the second ring sleeve, and the fourth ring sleeve is driven; the fourth ring receives the reverse torque T1 transmitted from the third fixing plate to the third ring and receives the pressure of the high-pressure gas in the piston ring groove in the axial direction, the resistance torque T2 of the high-pressure gas pressure to the fourth ring driven by the second ring is smaller than the reverse torque T1 of the fourth ring, so that the fourth ring drives the piston ring to move along the axial direction and compress the high-pressure gas under the driving of the second ring. Meanwhile, under the action of the one-way clutch ring, the third fixing plate cannot rotate along the direction opposite to the rotation direction of the input shaft, so that the third fixing plate is relatively fixed; at the moment, the rotation state of the gear is only autorotation; the self-rotating gear drives the output shaft to rotate through the gear ring and the disc. In the initial stage, since the distance from the axis of the driving bevel gear to the inner circle surface of the gear ring is 4 times of the distance from the axis of the gear to the inner circle surface of the gear ring, the gear can transmit larger torque, which is beneficial to the initial starting rotation of the output shaft of the speed changer.
With the output shaft rotating uniformly and the load being constant, the reverse torque T1 is constant at all times.
When the transmission is in a transition stage, the second annular sleeve is driven to rotate continuously by the continuous rotation of the input shaft; the continuous rotation of the second ring sleeve can drive the piston ring to continuously compress high-pressure gas; because the third fixing plate always has a reverse torque, as the piston ring continuously compresses high-pressure gas, the resistance torque T2 of the fourth ring sleeve driven by the second ring sleeve due to the pressure of the high-pressure gas is increased; when the torque resistance T2 is greater than the reverse torque T1 of the third fixing plate, the fourth ring sleeve cannot continuously compress high-pressure gas and is driven to rotate by the second ring sleeve, and then the third ring sleeve drives the first ring sleeve to rotate, so that the third fixing plate is driven to rotate by the input shaft, at the moment, the gear generates revolution motion, and the revolution motion enables the gear ring to rotate faster; under the condition that the rotating speed of the input shaft is not changed, the gear ring realizes torque reduction and speed increase. The revolution motion is triggered along with the accumulation of the compression amount of the high-pressure gas, so the influence of the revolution motion on the rotation speed pulsation of the input shaft is small, the impact of gear shifting on a power system is reduced, and the service life of the whole set of transmission system is prolonged. The total torque of T2 and the reverse torque T1 is T3, and the revolution of the ring gear is determined by T3.
The differential gear transmission consisting of the driving bevel gear, the two first bevel gears and the second bevel gear can ensure that the revolution motion of the gear does not influence the rotation motion of the gear.
When the connecting mechanism stops working, the second annular plate can drive the second annular sleeve to rotate in the direction under the reset action of the volute spiral spring, and then the fourth annular sleeve can be reset under the threaded fit. In the connecting mechanism, the spiral spring almost only participates in compression and reset, and almost does not transmit torque, so that the service life of the spiral spring is long, and the service life of the connecting mechanism is prolonged.
Compared with the traditional transmission technology, the beneficial effects of using the connecting mechanism to realize variable speed driving in the invention are as follows: the speed change effect is realized by using a simple structure, and meanwhile, the poking force is realized by depending on the compression of air pressure to the limit, so the formation of the poking force is realized step by step, when the poking force is greater than the resistance, the connecting mechanism can drive the first ring sleeve to rotate, and the design can not generate physical impact damage at the moment of gear shifting and speed changing, thereby greatly prolonging the service life of the speed changer; the invention utilizes the engagement of the driving bevel gear and other bevel gears to lead the gear to rotate, thus realizing the transmission of larger torque, and in addition, the gear revolves around the gear ring under the effect of gear shifting and speed increasing of the connecting structure, thus realizing the transmission of larger rotating speed under the double effects of rotation and revolution of the gear; the invention has simple structure and better use effect.
Drawings
Fig. 1 is a schematic view of the overall component distribution.
Fig. 2 is a schematic perspective view of an integral part.
Fig. 3 is a schematic sectional front view of the entire part.
Fig. 4 is a schematic cross-sectional view of the first housing.
Fig. 5 is a schematic view showing the mounting of the ring gear.
FIG. 6 is a one-way clutch ring installation schematic.
Fig. 7 is a gear installation schematic.
Fig. 8 is a schematic view of the connection mechanism.
Fig. 9 is a perspective schematic view of the connection mechanism.
Fig. 10 is a schematic cross-sectional view of the attachment mechanism.
Fig. 11 is a schematic sectional view of the second collar installation.
Fig. 12 is a schematic sectional view of the first ring plate installation.
FIG. 13 is a schematic view of an inner key guide channel and an outer key guide channel.
FIG. 14 is a schematic view of a wrap spring installation.
Fig. 15 is a schematic view of the driving bevel gear and gear rotation direction relationship.
FIG. 16 is a schematic of the torque variation of T1, T2, and T3.
Number designation in the figures: 1. a first housing; 2. an input shaft; 3. a connecting mechanism; 4. an output shaft; 5. a first loop; 6. a unidirectional clutch ring; 7. a first fixing plate; 8. a ring plate; 9. a second fixing plate; 10. a third fixing plate; 12. a fourth fixing plate; 13. a first shaft; 14. a second shaft; 15. a third axis; 16. a gear; 17. a ring gear; 18. a disc; 19. a cylindrical cavity; 20. a mechanism hole; 21. a shaft hole; 22. driving the bevel gear; 23. a first bevel gear; 24. a second taper tooth; 25. a third bevel gear; 26. a fourth bevel gear; 27. a fifth bevel gear; 28. a sixth bevel gear; 30. a second housing; 31. a second loop; 32. a volute spiral spring; 33. a third loop; 34. a fixing ring; 35. fixing the support plate; 36. a ring groove; 41. a fourth loop; 42. a first ring plate; 43. a piston ring; 45. a piston ring groove; 47. a second ring plate; 49. an internal bond; 50. an external bond; 51. an inner key guide groove; 52. outer key guide slot.
Detailed Description
As shown in fig. 1 and 2, it includes a first housing 1, an input shaft 2, a connecting mechanism 3, an output shaft 4, a first ring sleeve 5, a one-way clutch ring 6, a first fixing plate 7, a ring disc 8, a second fixing plate 9, a third fixing plate 10, a fourth fixing plate 12, a first shaft 13, a second shaft 14, a third shaft 15, a gear 16, a gear ring 17, a disc 18, a cylindrical cavity 19, a mechanism hole 20, a shaft hole 21, a driving bevel gear 22, a first bevel gear 23, a second bevel gear 24, a third bevel gear 25, a fourth bevel gear 26, a fifth bevel gear 27, and a sixth bevel gear 28, as shown in fig. 4, wherein the first housing 1 has the cylindrical cavity 19 therein; one side surface of the first shell 1 is provided with a mechanism hole 20, and the other side surface is provided with a shaft hole 21; as shown in fig. 3 and 6, one end of the input shaft 2 is provided with a driving bevel gear 22; as shown in fig. 3 and 5, the connecting mechanism 3 is mounted on the outer circumferential surface of the input shaft 2 and the connecting mechanism 3 is located in the mechanism hole 20; as shown in fig. 3 and 6, the first collar 5 is installed on the outer circumferential surface of the input shaft 2 between the connecting mechanism 3 and the driving bevel gear 22; the first ring sleeve 5 is connected with the connecting mechanism 3; the ring disc 8 is arranged at one end of the first ring sleeve 5 and is positioned between the first ring sleeve 5 and the driving bevel gear 22; a unidirectional clutch ring 6 is arranged on the outer circular surface of the first ring sleeve 5; two first fixing plates 7 are symmetrically arranged on the outer circular surface of the one-way clutch ring 6; one end of the first fixing plate 7, which is not connected with the one-way clutch ring 6, is connected with the inner cavity surface of the cylindrical cavity 19; two second fixing plates 9 are symmetrically arranged on the disc surface of the annular disc 8 close to the driving bevel gear 22; a third fixing plate 10 is arranged at one end of each of the two second fixing plates 9, which is not connected with the annular disc 8; two fourth fixing plates 12 are symmetrically arranged on the third fixing plate 10; as shown in fig. 3 and 7, two first bevel teeth 23 are mounted on the corresponding second fixing plate 9 through axial symmetry; the two first bevel teeth 23 are respectively meshed with the driving bevel teeth 22; a first shaft 13 is installed at the middle position of the third fixing plate 10; one end of the first shaft 13 is provided with a second bevel gear 24, and the other end is provided with a third bevel gear 25; the second conical teeth 24 are positioned between the two second fixing plates 9 and are respectively meshed with the two first conical teeth 23; a second shaft 14 is arranged on each of the two fourth fixing plates 12; one end of the second shaft 14 is provided with a fourth bevel gear 26, and the other end is provided with a fifth bevel gear 27; a third shaft 15 is installed at both ends of the third fixing plate 10; one end of the third shaft 15 is provided with a sixth bevel gear 28, and the other end is provided with a gear 16; the two fourth bevel teeth 26 are meshed with the third bevel teeth 25; the two fifth conical teeth 27 each mesh with a corresponding sixth conical tooth 28.
As shown in fig. 3 and 5, the output shaft 4 is mounted in the shaft hole 21; one end of the output shaft 4 is provided with a disc 18, and the disc 18 is positioned in a cylindrical cavity 19; the ring gear 17 is mounted on the disc 18 and is located in the cylindrical cavity 19; the second fixing plate 9, the third fixing plate 10, the fourth fixing plate 12 and the gear 16 are all positioned in the gear ring 17; the gear 16 meshes with a ring gear 17.
As shown in fig. 8 and 9, the above-mentioned connecting mechanism 3 includes a second housing 30, a second ring housing 31, a spiral spring 32, a third ring housing 33, a fixing ring 34, a ring groove 36, a fourth ring housing 41, a first ring plate 42, a piston ring 43, a piston ring groove 45, a second ring plate 47, an inner key 49, an outer key 50, an inner key guide groove 51, and an outer key guide groove 52, wherein the second housing 30 is mounted in the mechanism hole 20; as shown in fig. 10 and 11, the second collar 31 is mounted on the outer circumferential surface of the input shaft 2 and the outer circumferential surface of the second collar 31 is in contact with the inner wall surface of the second housing 30; a ring groove 36 is formed on one side surface of the second ring sleeve 31; the inner groove surface of the ring groove 36 is provided with threads; the second ring plate 47 is arranged on the side surface of the second ring sleeve 31 provided with the ring groove 36; as shown in fig. 10 and 13, the third annular sleeve 33 is mounted on the outer circumferential surface of the input shaft 2; a piston ring groove 45 is formed in the side face of one end of the third ring sleeve 33, and the other end of the third ring sleeve is connected with the first ring sleeve 5; one end of the third ring sleeve 33 provided with the piston ring groove 45 is positioned in the second ring plate 47; the inner circular surface of the piston ring groove 45 is symmetrically provided with two inner key guide grooves 51, and the outer circular surface is symmetrically provided with two outer key guide grooves 52; the fixing ring 34 is nested on the outer circular surface of the third ring sleeve 33; the outer circumferential surface of the fixing ring 34 is connected to the inner wall surface of the second housing 30; as shown in fig. 14, one end of spiral spring 32 is mounted on the inner circumferential surface of second collar plate 47, and the other end is mounted on the outer circumferential surface of third collar 33; as shown in fig. 10 and 12, the fourth collar 41 is mounted on the outer circumferential surface of the input shaft 2 and the fourth collar 41 has threads on the outer circumferential surface; the fourth ring sleeve 41 is positioned in the ring groove 36 of the second ring sleeve, and the threads on the fourth ring sleeve 41 are matched with the threads on the inner groove surface of the ring groove 36 of the second ring sleeve; one end of the first ring plate 42 is mounted on the side surface of the fourth ring sleeve 41, and the other end is mounted with a piston ring 43; two inner keys 49 are symmetrically arranged on the inner circular surface of the piston ring 43, and two outer keys 50 are symmetrically arranged on the outer circular surface; as shown in fig. 10 and 14, the piston ring 43 is located in the piston ring groove 45; the two inner keys 49 are located in respective inner key guide grooves 51, and the two outer keys 50 are located in respective outer key guide grooves 52; the piston ring 43 slides in the piston ring groove 45 by means of an inner key 49 and an outer key 50.
As shown in fig. 3, the distance between the two ends of the third fixing plate 10 and the corresponding second fixing plate 9 is equal.
As shown in fig. 3, the maximum diameter of the sixth conical tooth 28 is smaller than the diameter of the gear 16.
As shown in fig. 3, the distance from the axis of the driving bevel gear 22 to the inner circumferential surface of the ring gear 17 is 4 times the distance from the axis of the gear 16 to the inner circumferential surface of the ring gear 17.
As shown in fig. 3, the end of the input shaft 2, to which the driving bevel gear 22 is not attached, is connected to a power unit.
As shown in fig. 3, the end of the output shaft 4 not connected to the disc 18 is connected to an actuator.
High-pressure gas is filled between the piston ring 43 and the piston ring groove 45.
When the second ring 31 is not rotated, the distance between the piston ring 43 and the bottom surface of the third ring is maximized.
According to the invention, the unidirectional clutch ring 6 is arranged on the first ring sleeve 5, and the two first fixing plates 7 are symmetrically arranged on the unidirectional clutch ring 6, so that the first ring sleeve 5 is fixed and can rotate in the unidirectional clutch ring 6; the function of the unidirectional clutch ring 6 here is: in the driving direction, the first collar 5 can only rotate in a single direction and the direction of rotation is always the same as the direction of rotation of the input shaft 2.
The ring disc 8 is arranged on the first ring sleeve 5, the two second fixing plates 9 are symmetrically arranged on the ring disc 8, and the third fixing plate 10 is arranged on the second fixing plates 9, so that the first ring sleeve 5 can drive the second fixing plates 9 to rotate around the axis of the first ring sleeve 5 through the ring disc 8, and the second fixing plates 9 drive the third fixing plates 10 to rotate around the axis of the first ring sleeve 5.
As shown in fig. 15, the driving bevel gear 22 is engaged with the first bevel gear 23, the first bevel gear 23 is engaged with the second bevel gear 24, and the third bevel gear 25 and the second bevel gear 24 are both mounted on the first shaft 13, so that the driving bevel gear 22 can drive the third bevel gear 25 to rotate through the first bevel gear 23, the second bevel gear 24 and the first shaft 13, and the rotation direction of the third bevel gear 25 is opposite to that of the driving bevel gear 22; the third bevel gear 25 is meshed with the fourth bevel gear 26, the fourth bevel gear 26 and the fifth bevel gear 27 are both mounted on the second shaft 14, the fifth bevel gear 27 is meshed with the sixth bevel gear 28, the sixth bevel gear 28 and the gear 16 are both mounted on the third shaft 15, so that the third bevel gear 25 can drive the gear 16 to rotate through the fourth bevel gear 26, the second shaft 14, the fifth bevel gear 27, the sixth bevel gear 28 and the third shaft 15, and the rotation direction of the third bevel gear 25 is opposite to that of the gear 16; when the final drive bevel 22 is transmitted to the gear 16 via the respective bevel and shaft, the drive bevel 22 rotates in the same direction as the gear 16.
The gear 16 meshes with the ring gear 17, so that the gear 16 can rotate the output shaft 4 via the ring gear 17 and the disc 18.
The distance from the axis of the driving bevel gear 22 to the inner circle surface of the gear ring 17 is 4 times of the distance from the axis of the gear 16 to the inner circle surface of the gear ring 17, and the design is favorable for transmitting larger transmission ratio.
In the above-described connection mechanism 3, the second housing 30 is mounted in the mechanism hole 20, and then the second housing 30 is fixed; the second ring sleeve 31 is arranged on the input shaft 2, so that the input shaft 2 can drive the second ring sleeve 31 to rotate; the third ring 33 is mounted on the outer circumferential surface of the input shaft 2 and the outer circumferential surface of the third ring 33 is nested with the fixing ring 34, so that the third ring 33 is fixed by the fixing ring 34 and can rotate in the fixing ring 34; third loop 33 is connected to first loop 5 so that third loop 33 rotates first loop 5. The inner surface of the ring groove 36 in the second ring sleeve 31 is provided with threads, the outer surface of the fourth ring sleeve 41 is provided with threads, the threads on the inner surface of the ring groove 36 and the threads on the outer surface of the fourth ring sleeve 41 are installed in the ring groove 36 in a thread matching mode, and then through the rotation of the second ring sleeve 31, the fourth ring sleeve 41 can move axially in the direction away from the ring groove 36 under the condition that the fourth ring sleeve 41 does not rotate; one end of the first ring plate 42 is mounted on the fourth ring sleeve 41, and the other end is mounted with the piston ring 43, so that the fourth ring sleeve 41 can drive the piston ring 43 to axially move towards the piston ring groove 45 through the first ring plate 42; the piston ring 43 is provided with an inner key 49 and an outer key 50, the inner key 49 slides in the inner key guide groove 51, the outer key 50 slides in the outer key guide groove 52, and the matching of the keys and the key grooves enables the fourth ring sleeve 41 and the third ring sleeve 33 to be synchronous in the rotation direction; as the piston ring 43 is compressed into the piston ring groove 45, the high-pressure gas in the piston ring groove 45 is compressed. The scroll spring 32 serves to restore the second and fourth collars 31 and 41.
The specific implementation mode is as follows: when the input shaft 2 is not rotationally operated, the distance between the piston ring 43 and the piston ring groove 45 is maximized while the wrap spring 32 is in an uncompressed state.
When the input shaft 2 rotates, in the initial stage, the input shaft 2 drives the driving bevel gear 22 to rotate, the driving gear 16 drives the gear 16 to rotate through the first bevel gear 23, the second bevel gear 24, the third bevel gear 25, the fourth bevel gear 26, the fifth bevel gear 27 and the sixth bevel gear 28, when the gear 16 rotates, according to the interaction of forces, the gear ring 17 provides a reverse torque T1 for the gear 16, and the reverse torque T1 is transmitted to the third fixing plate 10 through the third shaft 15, so that the third fixing plate 10 has a movement trend opposite to the rotation direction of the input shaft 2; meanwhile, the input shaft 2 is matched with the thread of the fourth ring sleeve 41 through the second ring sleeve 31, and a driving effect is generated on the fourth ring sleeve 41; initially, the fourth ring 41 is subjected to the reverse torque T1 transmitted from the third fixing plate 10 to the third ring 33 and is subjected to the pressure of the high-pressure gas in the piston ring groove 45 in the axial direction, and the resisting torque T2 of the high-pressure gas pressure to the fourth ring 41 driven by the second ring 31 is smaller than the reverse torque T1 of the fourth ring 41, so that the fourth ring 41 drives the piston ring 43 to move along the axial direction and compress the high-pressure gas under the driving of the second ring 31. Meanwhile, under the action of the one-way clutch ring 6, the third fixing plate 10 cannot rotate along the direction opposite to the rotation direction of the input shaft 2, so that the third fixing plate 10 is relatively fixed; at this time, the rotation state of the gear 16 is only autorotation; the rotating gear 16 drives the output shaft 4 to rotate through the gear ring 17 and the disc 18. In the initial phase, since the distance from the axis of the driving bevel 22 to the inner circumferential surface of the ring gear 17 is 4 times the distance from the axis of the gear 16 to the inner circumferential surface of the ring gear 17, the gear 16 transmits a large torque, which is advantageous for the initial starting rotation of the output shaft 4 of the transmission.
As shown in fig. 16 (a), when the output shaft 4 rotates uniformly and the load is constant, the reverse torque T1 is constant at all times.
When the transmission is in a transition stage, which requires a large torque and then needs to obtain a large output rotating speed, the continuous rotation of the input shaft 2 drives the second annular sleeve 31 to continuously rotate; the continuous rotation of the second ring sleeve 31 drives the piston ring 43 to continuously compress high-pressure gas; as shown in fig. 16 (b), since there is always a reverse torque in the third fixing plate 10, as the piston ring 43 continues to compress the high-pressure gas, the resistance torque T2 of the high-pressure gas pressure to the fourth sleeve 41 driven by the second sleeve 31 also increases; when the torque resistance T2 is greater than the reverse torque T1 of the third fixing plate 10, the fourth ring sleeve 41 will not compress the high-pressure gas, but will be driven by the second ring sleeve 31 to rotate, and further the third ring sleeve 33 will drive the first ring sleeve 5 to rotate, so that the third fixing plate 10 is driven by the input shaft 2 to rotate, and at this time, the gear 16 generates the revolution motion, and the revolution motion makes the gear 17 rotate faster; the ring gear 17 achieves torque reduction and speed increase without changing the rotational speed of the input shaft 2. The revolution motion is triggered along with the accumulation of the compression amount of the high-pressure gas, so the influence of the revolution motion on the rotation speed pulsation of the input shaft 2 is small, the impact of gear shifting on a power system is reduced, and the service life of the whole set of transmission system is prolonged. As shown in fig. 16 (c), the total torque of T2 and the reverse torque T1 is T3, and the revolution of the ring gear 17 is determined by T3.
The differential gear 16 transmission composed of the driving bevel gear 22, the two first bevel gears 23 and the second bevel gear 24 designed in the invention can ensure that the revolution motion of the gear 16 does not influence the rotation motion of the gear 16.
When the connection mechanism 3 stops working, the second ring plate 47 can drive the second ring sleeve 31 to rotate under the reset action of the spiral spring 32, and then the fourth ring sleeve 41 can be reset under the screw-thread fit. In the connecting mechanism 3, the spiral spring 32 is almost only involved in compression and return, and almost no torque is transmitted, so that the service life of the spiral spring 32 is long, thereby extending the service life of the connecting mechanism 3.
In conclusion, the invention has the main beneficial effects that: the connecting mechanism 3 used for realizing variable speed driving in the invention has the advantages that: the speed change effect is realized by using a simple structure, meanwhile, the poking force is realized by depending on the compression of air pressure to the limit, so the formation of the poking force is realized step by step, when the poking force is greater than the resistance, the connecting mechanism 3 can drive the first ring sleeve 5 to rotate, and the design can not generate physical impact damage at the moment of gear shifting and speed changing, thereby greatly prolonging the service life of the speed changer; the invention utilizes the engagement of the driving bevel gear 22 and other bevel gears to lead the gear 16 to rotate, thus realizing the transmission of larger torque, and in addition, the gear 16 revolves around the gear ring 17 under the effect of gear shifting and speed increasing of the connecting structure, and the transmission of larger rotating speed is realized under the double effects of rotation and revolution of the gear 16; the invention has simple structure and better use effect.
Claims (5)
1. An impact resistant transmission characterized by: the device comprises a first shell, an input shaft, a connecting mechanism, an output shaft, a first ring sleeve, a one-way clutch ring, a first fixing plate, a ring disc, a second fixing plate, a third fixing plate, a fourth fixing plate, a first shaft, a second shaft, a third shaft, a gear ring, a disc, a cylindrical cavity, a mechanism hole, a shaft hole, a driving bevel gear, a first bevel gear, a second bevel gear, a third bevel gear, a fourth bevel gear, a fifth bevel gear and a sixth bevel gear, wherein the cylindrical cavity is formed in the first shell; one side surface of the first shell is provided with a mechanism hole, and the other side surface of the first shell is provided with a shaft hole; one end of the input shaft is provided with a driving bevel gear; the outer circular surface of the input shaft is provided with a connecting mechanism, and the connecting mechanism is positioned in the mechanism hole; the first ring sleeve is arranged on the outer circular surface of the input shaft and is positioned between the connecting mechanism and the driving bevel gear; the first ring sleeve is connected with the connecting mechanism; the ring disc is arranged at one end of the first ring sleeve and is positioned between the first ring sleeve and the driving bevel gear; a unidirectional clutch ring is arranged on the outer circular surface of the first ring sleeve; two first fixing plates are symmetrically arranged on the outer circular surface of the one-way clutch ring; one end of the first fixing plate, which is not connected with the one-way clutch ring, is connected with the inner cavity surface of the cylindrical cavity; two second fixing plates are symmetrically arranged on the disc surface of the annular disc close to the driving bevel gear; one ends of the two second fixing plates, which are not connected with the annular disc, are provided with third fixing plates; two fourth fixing plates are symmetrically arranged on the third fixing plate; the two first bevel gears are symmetrically arranged on the corresponding second fixing plates through axes; the two first bevel gears are respectively meshed with the driving bevel gears; a first shaft is arranged in the middle of the third fixing plate; one end of the first shaft is provided with a second bevel gear, and the other end of the first shaft is provided with a third bevel gear; the second bevel gear is positioned between the two second fixing plates and is respectively meshed with the two first bevel gears; a second shaft is arranged on each of the two fourth fixing plates; one end of the second shaft is provided with a fourth bevel gear, and the other end of the second shaft is provided with a fifth bevel gear; a third shaft is arranged at the two ends of the third fixing plate; one end of the third shaft is provided with a sixth bevel gear, and the other end of the third shaft is provided with a gear; the two fourth bevel gears are meshed with the third bevel gear; the two fifth bevel teeth are respectively meshed with the corresponding sixth bevel teeth;
the output shaft is arranged in the shaft hole; one end of the output shaft is provided with a disc which is positioned in the cylindrical cavity; the gear ring is arranged on the disc and positioned in the cylindrical cavity; the second fixing plate, the third fixing plate, the fourth fixing plate and the gear are all positioned in the gear ring; the gear is meshed with the gear ring;
the connecting mechanism comprises a second shell, a second ring sleeve, a volute spiral spring, a third ring sleeve, a fixing ring, a ring groove, a fourth ring sleeve, a first ring plate, a piston ring groove, a second ring plate, an inner key, an outer key, an inner key guide groove and an outer key guide groove, wherein the second shell is arranged in a mechanism hole; the second ring sleeve is arranged on the outer circular surface of the input shaft, and the outer circular surface of the second ring sleeve is in contact with the inner wall surface of the second shell; one side surface of the second ring sleeve is provided with a ring groove; the inner groove surface of the ring groove is provided with threads; the second ring plate is arranged on the side surface of the second ring sleeve with the ring groove; the third ring sleeve is arranged on the outer circular surface of the input shaft; a piston ring groove is formed in the side face of one end of the third ring sleeve, and the other end of the third ring sleeve is connected with the first ring sleeve; one end of the third ring sleeve, which is provided with the piston ring groove, is positioned in the second ring plate; two inner key guide grooves are symmetrically formed in the inner circular surface of the piston ring groove, and two outer key guide grooves are symmetrically formed in the outer circular surface of the piston ring groove; the fixing ring is nested on the outer circular surface of the third ring sleeve; the outer circular surface of the fixing ring is connected with the inner wall surface of the second shell; one end of the volute spiral spring is arranged on the inner circular surface of the second ring plate, and the other end of the volute spiral spring is arranged on the outer circular surface of the third ring sleeve; the fourth ring sleeve is arranged on the outer circular surface of the input shaft, and the outer circular surface of the fourth ring sleeve is provided with threads; the fourth ring sleeve is positioned in the ring groove of the second ring sleeve, and the threads on the fourth ring sleeve are matched with the threads on the inner groove surface of the ring groove of the second ring sleeve; one end of the first ring plate is arranged on the side surface of the fourth ring sleeve, and the other end of the first ring plate is provided with a piston ring; two inner keys are symmetrically arranged on the inner circular surface of the piston ring, and two outer keys are symmetrically arranged on the outer circular surface; the piston ring is positioned in the piston ring groove; the two inner keys are respectively positioned in the corresponding inner key guide grooves, and the two outer keys are respectively positioned in the corresponding outer key guide grooves; the piston ring slides in the piston ring groove through the inner key and the outer key;
the distances between the two ends of the third fixing plate and the corresponding second fixing plate are equal;
the maximum diameter of the sixth bevel gear is smaller than the diameter of the gear;
the distance from the axis of the driving bevel gear to the inner circle surface of the gear ring is 4 times of the distance from the axis of the gear to the inner circle surface of the gear ring.
2. An impact-resistant transmission as recited in claim 1, wherein: and one end of the input shaft, which is not provided with the driving bevel gear, is connected with the power device.
3. An impact-resistant transmission as recited in claim 1, wherein: and one end of the output shaft, which is not connected with the disc, is connected with the actuating mechanism.
4. An impact-resistant transmission as recited in claim 1, wherein: high-pressure gas is filled between the piston ring and the piston ring groove.
5. An impact-resistant transmission as recited in claim 1, wherein: when the second ring is not rotated, the distance between the piston ring and the bottom surface of the third ring is maximized.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910738133.1A CN110439993B (en) | 2018-03-21 | 2018-03-21 | Shock-resistant transmission |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910738133.1A CN110439993B (en) | 2018-03-21 | 2018-03-21 | Shock-resistant transmission |
| CN201810237261.3A CN108443487B (en) | 2018-03-21 | 2018-03-21 | A kind of shock resistance speed changer |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810237261.3A Division CN108443487B (en) | 2018-03-21 | 2018-03-21 | A kind of shock resistance speed changer |
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| Publication Number | Publication Date |
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| CN110439993A CN110439993A (en) | 2019-11-12 |
| CN110439993B true CN110439993B (en) | 2021-01-29 |
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| CN201910738198.6A Active CN110332309B (en) | 2018-03-21 | 2018-03-21 | Impact-resistant transmission |
| CN201910738133.1A Active CN110439993B (en) | 2018-03-21 | 2018-03-21 | Shock-resistant transmission |
| CN201810237261.3A Active CN108443487B (en) | 2018-03-21 | 2018-03-21 | A kind of shock resistance speed changer |
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| CN201910738198.6A Active CN110332309B (en) | 2018-03-21 | 2018-03-21 | Impact-resistant transmission |
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| CN201810237261.3A Active CN108443487B (en) | 2018-03-21 | 2018-03-21 | A kind of shock resistance speed changer |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN108443487B (en) | 2019-09-24 |
| CN110332309A (en) | 2019-10-15 |
| CN110332309B (en) | 2020-12-01 |
| CN110439993A (en) | 2019-11-12 |
| CN108443487A (en) | 2018-08-24 |
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Effective date of registration: 20221208 Address after: 215500 Mingjing Village, Changfu Street, Changshu City, Suzhou City, Jiangsu Province Patentee after: Changshu Darun Precision Machinery Co.,Ltd. Address before: 310003 rooms 401 and 402, unit 2, 155 Mashi street, Shangcheng District, Hangzhou City, Zhejiang Province Patentee before: HANGZHOU QIZHEN INTELLECTUAL PROPERTY CONSULTING CO.,LTD. |