CN111322367A - Speed changing device - Google Patents
Speed changing device Download PDFInfo
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- CN111322367A CN111322367A CN202010269184.7A CN202010269184A CN111322367A CN 111322367 A CN111322367 A CN 111322367A CN 202010269184 A CN202010269184 A CN 202010269184A CN 111322367 A CN111322367 A CN 111322367A
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- ring
- gear
- bevel gear
- shaft
- ring sleeve
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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
- F16H33/00—Gearings based on repeated accumulation and delivery of energy
- F16H33/02—Rotary transmissions with mechanical accumulators, e.g. weights, springs, intermittently-connected flywheels
- F16H33/04—Gearings for conveying rotary motion with variable velocity ratio, in which self-regulation is sought
- F16H33/06—Gearings for conveying rotary motion with variable velocity ratio, in which self-regulation is sought based essentially on spring action
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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
- F16H57/00—General details of gearing
- F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Rotary Pumps (AREA)
Abstract
The invention belongs to the technical field of transmissions, and particularly relates to a speed change device 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, a volute spiral spring and the like, wherein the volute spiral spring in the connecting mechanism is used for realizing speed change driving, and the speed change device has the beneficial effects that: the speed change effect is realized by using a simple structure, and simultaneously, as the poking force provided by the spiral spring is continuous, the physical impact damage can not be generated at the moment of gear shifting and speed changing, so that the service life of the speed changer is greatly prolonged; 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 a speed change device.
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 present invention is directed to a transmission that solves the above problems.
Disclosure of Invention
In order to solve the above-mentioned defects in the prior art, the present invention discloses a speed changing device, which is realized by adopting the following technical scheme.
A transmission device 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 meets the condition that the larger the phase angle between the input shaft and the first ring sleeve is, the larger the torque transmitted by the input shaft to the first ring sleeve is.
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 of the present technique, the above-mentioned scroll spring is made of 60Si2MnA steel.
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 present technology, the connecting mechanism includes a second housing, a second collar, a volute spring, a third collar, a fixing ring, a fixing support plate, and a ring groove, wherein the second housing is mounted in the 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 third ring sleeve is nested on the outer circular surface of the input shaft; one end of the third ring sleeve is positioned in the ring sleeve, and the other end of the third ring sleeve is connected with the first ring sleeve; a fixing ring is arranged on the outer circular surface of the third ring sleeve; the fixing ring is arranged on the inner wall surface of the second shell through two fixing support plates; one end of the spiral spring is arranged on the inner groove surface of the ring groove, and the other end of the spiral spring is arranged on the outer circular surface of the third ring sleeve.
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 scroll spring of the invention has the following functions: on one hand, when the input shaft starts to provide power, a large phase angle exists between the second ring sleeve and the third ring sleeve, and the spiral spring is rotated, compressed and stored with energy; on the other hand, after the resistance of the third ring sleeve is overcome by the spiral spring, the second ring sleeve can drive the third ring sleeve to rotate through the spiral spring, and then the first ring sleeve is driven to rotate.
When the input shaft does not rotate, the scroll spring is in a state of being not compressed to store energy.
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 drives the volute spiral spring to rotate through the second ring sleeve to compress and store energy, at the beginning of the rotation and compression and energy storage of the volute spiral spring, the restoring torque of the volute spiral spring is smaller and smaller than the reaction torque of the third fixing plate, and 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 scroll spring to continuously compress and store energy; because the third fixed plate always has a reverse torque, the spiral spring toggle torque T2 is increased along with the continuous rotation and compression of the spiral spring; when the toggle torque T2 of the volute spiral spring is greater than the reverse torque T1 of the third fixed plate, the third fixed plate is driven by the input shaft to rotate through the volute spiral spring, 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 continuous compression of the scroll spring, 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 load of the input shaft and the output shaft disappears, the scroll spring is reset.
Compared with the traditional transmission technology, the invention uses the spiral spring in the connecting mechanism to realize variable speed driving, and has the advantages that: the speed change effect is realized by using a simple structure, and simultaneously, as the poking force provided by the spiral spring is continuous, the physical impact damage can not be generated at the moment of gear shifting and speed changing, so that the service life of the speed changer is greatly prolonged; 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 second collar installation schematic.
FIG. 12 is a schematic view of a scroll spring installation.
Fig. 13 is a fixing ring mounting diagram.
Fig. 14 is a schematic view of the driving bevel gear in relation to the direction of rotation of the gear.
FIG. 15 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. and a ring groove.
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.
The connecting mechanism 3 satisfies that the larger the phase angle between the input shaft 2 and the first collar 5 is, the larger the torque transmitted from the input shaft 2 to the first collar 5 is.
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.
The scroll spring 32 is made of 60Si2MnA steel.
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.
The end of the input shaft 2, which is not provided with the driving bevel gear 22, is connected with a power device.
The end of the output shaft 4 not connected with the disc 18 is connected with an actuating mechanism.
As shown in fig. 8 and 9, the 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 fixing support plate 35, and a ring groove 36, 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 third ring sleeve 33 is nested on the outer circular surface of the input shaft 2; one end of the third loop 33 is located in the loop, and the other end is connected to the first loop 5; as shown in fig. 10 and 13, a fixing ring 34 is mounted on the outer circumferential surface of the third loop 33; the fixing ring 34 is mounted on the inner wall surface of the second housing 30 via two fixing support plates 35; as shown in fig. 10 and 12, one end of spiral spring 32 is mounted on the inner surface of annular groove 36, and the other end is mounted on the outer circumferential surface of third collar 33.
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. 14, 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 scroll spring 32 of the present invention functions as: on one hand, when the input shaft 2 is just started to provide power, a large phase angle exists between the second ring sleeve 31 and the third ring sleeve 33, and the scroll spring 32 is rotated to compress and store energy; on the other hand, when the resistance of the third ring 33 is overcome by the spiral spring 32, the second ring 31 can drive the third ring 33 to rotate through the spiral spring 32, and further drive the first ring 5 to rotate.
When the input shaft 2 is not rotating, the spiral spring 32 is in a state of not being compressed and storing energy.
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 drives the scroll spring 32 to rotate through the second ring sleeve 31 to compress and store energy, at the beginning of the rotation and compression and energy storage of the scroll spring 32, the restoring torque of the scroll spring 32 is smaller and smaller than the reaction torque of the third fixing plate 10, and 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. 15 (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 scroll spring 32 to continuously compress and store energy; as shown in fig. 15 (b), since there is always a reverse torque on the third fixing plate 10, as the spiral spring 32 continues to rotate and compress, the toggle torque T2 of the spiral spring 32 increases; when the torque T2 dialed by the spiral spring 32 is greater than the reverse torque T1 of the third fixing plate 10, the third fixing plate 10 is driven by the input shaft 2 to rotate through the spiral spring 32, and at this time, the gear 16 generates revolution motion, and the revolution motion makes the ring 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 continuous compression of the scroll spring 32, 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. 15 (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.
The specific implementation mode is as follows: when the drive of the input shaft 2 and the load of the output shaft 4 are removed, the scroll spring 32 is restored.
In conclusion, the invention has the main beneficial effects that: the beneficial effects of using the spiral spring 32 in the connecting mechanism 3 to realize variable speed driving in the invention are as follows: the speed change effect is realized by using a simple structure, and simultaneously, as the poking force provided by the spiral spring 32 is continuous, the physical impact damage can not be generated 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. A transmission device 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 meets the condition that the larger the phase angle between the input shaft and the first ring sleeve is, the larger the torque transmitted by the input shaft to the first ring sleeve is;
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;
one end of the input shaft, which is not provided with the driving bevel gear, is connected with a power device;
and one end of the output shaft, which is not connected with the disc, is connected with the actuating mechanism.
2. A transmission as claimed in claim 1, wherein: the distance between the two ends of the third fixing plate and the corresponding second fixing plate is equal.
3. A transmission as claimed in claim 1, wherein: the maximum diameter of the sixth bevel gear is smaller than the diameter of the gear.
4. A transmission as claimed in claim 1, wherein: the connecting mechanism comprises a second shell, a second ring sleeve, a volute spiral spring, a third ring sleeve, a fixing ring, a fixing support plate and a ring groove, wherein the second shell is arranged in the 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 third ring sleeve is nested on the outer circular surface of the input shaft; one end of the third ring sleeve is positioned in the ring sleeve, and the other end of the third ring sleeve is connected with the first ring sleeve; a fixing ring is arranged on the outer circular surface of the third ring sleeve; the fixing ring is arranged on the inner wall surface of the second shell through two fixing support plates; one end of the spiral spring is arranged on the inner groove surface of the ring groove, and the other end of the spiral spring is arranged on the outer circular surface of the third ring sleeve.
5. A transmission as claimed in claim 4, wherein: the scroll spring is made of 60Si2MnA steel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010269184.7A CN111322367A (en) | 2018-03-21 | 2018-03-21 | Speed changing device |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010269184.7A CN111322367A (en) | 2018-03-21 | 2018-03-21 | Speed changing device |
| CN201810237262.8A CN108413018B (en) | 2018-03-21 | 2018-03-21 | Speed changer |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810237262.8A Division CN108413018B (en) | 2018-03-21 | 2018-03-21 | Speed changer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN111322367A true CN111322367A (en) | 2020-06-23 |
Family
ID=63133190
Family Applications (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010268940.4A Active CN111306274B (en) | 2018-03-21 | 2018-03-21 | Speed changing equipment |
| CN201810237262.8A Active CN108413018B (en) | 2018-03-21 | 2018-03-21 | Speed changer |
| CN202010269184.7A Withdrawn CN111322367A (en) | 2018-03-21 | 2018-03-21 | Speed changing device |
Family Applications Before (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010268940.4A Active CN111306274B (en) | 2018-03-21 | 2018-03-21 | Speed changing equipment |
| CN201810237262.8A Active CN108413018B (en) | 2018-03-21 | 2018-03-21 | Speed changer |
Country Status (1)
| Country | Link |
|---|---|
| CN (3) | CN111306274B (en) |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE69416968T2 (en) * | 1993-12-27 | 1999-09-30 | Nsk Ltd., Tokio/Tokyo | Power steering |
| CN1779293A (en) * | 2004-11-21 | 2006-05-31 | 庄建龙 | Speed variator structure |
| CN101566141A (en) * | 2008-11-30 | 2009-10-28 | 王鑫弘 | Mechanical capability motion machine |
| CN103968014A (en) * | 2014-03-31 | 2014-08-06 | 刘建 | Planet gear automatic gearbox of mining robot |
| CN203926675U (en) * | 2014-06-11 | 2014-11-05 | 杭州前进齿轮箱集团股份有限公司 | A kind of planet difference speed reducer used for electric vehicle |
| CN105240463A (en) * | 2015-10-21 | 2016-01-13 | 安徽星瑞齿轮传动有限公司 | Five-speed manual transmission assembly |
| CN106523606B (en) * | 2016-11-04 | 2019-03-15 | 浙江大众齿轮有限公司 | A kind of Multilayer-tooth geared automated gearbox based on scroll spring |
| CN107489743B (en) * | 2017-09-26 | 2020-08-04 | 浙江中马传动股份有限公司 | Automatic transmission |
-
2018
- 2018-03-21 CN CN202010268940.4A patent/CN111306274B/en active Active
- 2018-03-21 CN CN201810237262.8A patent/CN108413018B/en active Active
- 2018-03-21 CN CN202010269184.7A patent/CN111322367A/en not_active Withdrawn
Also Published As
| Publication number | Publication date |
|---|---|
| CN111306274B (en) | 2021-04-30 |
| CN108413018A (en) | 2018-08-17 |
| CN108413018B (en) | 2020-05-15 |
| CN111306274A (en) | 2020-06-19 |
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Legal Events
| Date | Code | Title | Description |
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| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WW01 | Invention patent application withdrawn after publication |
Application publication date: 20200623 |
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| WW01 | Invention patent application withdrawn after publication |